WO2022107649A1

WO2022107649A1 - Centrifugal blower for vehicle

Info

Publication number: WO2022107649A1
Application number: PCT/JP2021/041265
Authority: WO
Inventors: 亮介金森; 久善吉崎; 敬介原; 直人林
Original assignee: 株式会社ヴァレオジャパン
Priority date: 2020-11-17
Filing date: 2021-11-10
Publication date: 2022-05-27

Abstract

[Problem] To make it possible to reduce the risk of inside air mixing with outside air when an air conditioner is operating in an inside/outside air two-layer flow mode. [Solution] This centrifugal blower (1) comprises a first impeller (3), a second impeller (5), and a separation tube (30). An outlet-side end (33) of the separation tube 30 has a first turning surface (34) which turns a first air flow passing through the outside of the separation tube (30) outward in the radial direction. A distance (D1) between an end (46) of an inner edge (41) of a first blade (4) of the first impeller (3) and an edge (35) of the first turning surface (34) is longer than a distance (D2) between an end (65) of an inner edge (61) of a second blade (6) of the second impeller (5) and the edge (35) of the first turning surface (34).

Description

Centrifugal blower for vehicles

The present invention relates to a centrifugal blower applied to a two-phase flow type vehicle air conditioner.

Centrifugal blowers applied to vehicle air conditioners include a spiral scroll housing, an impeller housed in the scroll housing, a motor that drives the impeller to rotate, and a separator tube inserted inside the impeller. Centrifugal blowers equipped with are known. In such a centrifugal blower, when the vehicle air conditioner is operated in the inside / outside air two-phase flow mode, the outside air is flowed to the upper layer of the scroll housing and the inside air is flowed to the lower layer. The upper half of the impeller and the lower half of the impeller are separated by a circumferential dividing member so that the outside air and the inside air are separated from each other. Further, the internal space of the scroll housing is divided into an upper air flow path and a lower air flow path by a circumferential partition wall. Generally, the lower end of the separation cylinder, the dividing member, and the partition wall are arranged at the same position in the axial direction. When the air conditioner is operated in the inside / outside air two-phase flow mode, the outside air and the inside air introduced into the centrifugal blower by the rotation of the impeller are guided by the separation cylinder and the split member, and are respectively in the upper layer of the scroll housing. It flows into the air flow path and the lower air flow path.

Here, when the two-layer flow type vehicle air conditioner is operated in the inside / outside air two-layer flow mode, the ventilation resistance of the lower layer air flow path is increased by the arrangement of the temperature control door and the outlet door of the air conditioner. It is higher than the ventilation resistance of the air flow path. As a result, a part of the inside air flowing through the lower air flow path may flow into the upper air flow path through which the outside air flows. If the dry outside air and the moist inside air are mixed in, there is a possibility that it is difficult to secure the window clearness in the vehicle interior.

In the centrifugal blower disclosed in Patent Document 1 in order to prevent the inside air from being mixed in when the vehicle air conditioner is operated in the inside / outside air two-phase flow mode, the split member is radially more than the blade row. It extends outward to the bottom of the partition wall. As a result, when the air conditioner is operated in the inside / outside air two-phase flow mode, the inside air blown out from the blade row in the lower half of the impeller passes through the gap between the dividing member and the partition wall, and the air flow path on the outside air side of the upper layer. It is prevented from flowing into.

However, in the method disclosed in Patent Document 1, there is a possibility that the inside air may be mixed with the outside air through the gap between the separation cylinder and the dividing member.

Japanese Unexamined Patent Publication No. 2019-44739

The present invention is a centrifugal blower applied to a two-phase flow type vehicle air conditioner, and when the air conditioner is operated in the inside / outside air two-phase flow mode, the wet inside air is generated between the separation cylinder and the split member. It is an object of the present invention to provide a centrifugal blower that reduces the risk of being mixed with dry outside air through the space.

According to a preferred embodiment of the invention

It is a one-suction type centrifugal blower for vehicles.

With the motor

It has a plurality of first blades forming the first blade row in the circumferential direction, and is rotationally driven by the motor around a rotation axis extending in the axial direction to radially air air in the space inside the radial direction of the first blade row. The first impeller that blows out to the outside,

It has a plurality of second blades forming the second blade row in the circumferential direction, and is rotationally driven by the motor around the rotation axis to direct the air in the space inside the radial direction of the second blade row to the outside in the radial direction. The second impeller that blows out

A dividing member formed in a circumferential shape between the first wing row and the second wing row and dividing the space between the plurality of first wings and the space between the plurality of second wings.

A scroll housing having an internal space for accommodating the first impeller and the second impeller, a suction port opening on one end side in the axial direction, and a discharge port opening in the circumferential direction.

A region of the internal space of the scroll housing between the inner peripheral surface of the scroll housing and the outer peripheral surfaces of the first impeller and the second impeller, and the internal space of the discharge port in the axial direction. A partition wall that is divided to form a first air flow path facing the first blade row and a second air flow path facing the second blade row.

A separation cylinder extending in the axial direction through the radial inside of the suction port and the radial inside of the first blade row, and the flow of air sucked from the suction port into the scroll housing is separated. The first air flow is provided so as to be divided into a first air flow passing through the outside of the separation cylinder and a second air flow passing through the inside of the separation cylinder, and the first air flow is turned outward in the radial direction. A separation cylinder having an outlet-side end that guides the second air flow to the flow path and guides the second air flow outward in the radial direction to the second air flow path.

The first wing row is located on one side of the split member in the axial direction.

The second wing row is located on the other side of the split member in the axial direction.

The outlet-side end of the separation cylinder has a first turning surface that turns the first air flow outward in the radial direction, and a second turning surface that turns the second air flow outward in the radial direction. Have,

The first wing has an inner edge of the first wing that faces inward in the radial direction.

The second wing has an inner edge of the second wing that faces inward in the radial direction.

The distance between the other side end portion of the inner edge of the first wing in the axial direction and the outer edge portion of the first turning surface in the radial direction is the one side end of the inner edge of the second wing in the axial direction. Provided is a centrifugal blower that is longer than the distance between the portion and the radial outer edge of the first turning surface.

According to the embodiment of the present invention, it is a centrifugal blower applied to a two-phase flow type vehicle air conditioner, and when the air conditioner is operated in the inside / outside air two-phase flow mode, the wet inside air is separated from the separation cylinder. It is possible to provide a centrifugal blower in which the risk of mixing with dry outside air through the gap between the split member and the split member is suppressed.

It is a figure which shows the structure of the air intake part and the centrifugal blower of the air conditioner for a vehicle, and is the vertical sectional view which includes the meridional cross section of the centrifugal blower. FIG. 3 is a meridional cross-sectional view of a vehicle air conditioner cut at a cut surface orthogonal to the cut surface in FIG. 1. It is a meridional cross-sectional view which shows the main part of the centrifugal blower which concerns on 1st Embodiment. It is a figure corresponding to FIG. 3, and is the meridional cross-sectional view which shows the main part of the centrifugal blower which concerns on the modification of 1st Embodiment. It is a figure corresponding to FIG. 3, and is the meridional cross-sectional view which shows the main part of the centrifugal blower which concerns on 2nd Embodiment. It is a figure corresponding to FIG. 5, and is the meridional cross-sectional view which shows the main part of the centrifugal blower which concerns on the modification of 2nd Embodiment. It is a figure corresponding to FIG. 3, and is the meridional cross-sectional view which shows the main part of the centrifugal blower which concerns on 3rd Embodiment. It is a figure corresponding to FIG. 7, and is the meridional cross-sectional view which shows the main part of the centrifugal blower which concerns on the modification of 3rd Embodiment. It is a figure corresponding to FIG. 3, and is the meridional cross-sectional view which shows the main part of the centrifugal blower which concerns on 4th Embodiment. It is a figure corresponding to FIG. 9, and is the meridional cross-sectional view which shows the main part of the centrifugal blower which concerns on the modification of 4th Embodiment. It is a figure corresponding to FIG. 9, and is the meridional cross-sectional view which shows the main part of the centrifugal blower which concerns on 5th Embodiment. It is a figure corresponding to FIG. 8, and is the meridional cross-sectional view which shows the main part of the centrifugal blower which concerns on 6th Embodiment. It is a partially enlarged view of the meridian cross section of a separation cylinder, and is the figure which shows the edge part of the exit side end part.

[First Embodiment]

The first embodiment of the present invention will be described below with reference to the accompanying drawings.

1 and 2 are cross-sectional views showing the structure of an air intake portion and a centrifugal blower of an air conditioner according to the first embodiment. Further, FIG. 3 is an enlarged view showing a region surrounded by a two-dot chain line indicated by reference numeral III in FIG. 1.

The centrifugal blower 1 of the first embodiment is a single-suction type centrifugal blower used in a two-phase flow type vehicle air conditioner. The air conditioner has a defroster outlet (not shown), a vent outlet (not shown), and a foot outlet (not shown), and from each outlet, the windshield of the vehicle and the upper body of the occupant. And it is designed to blow air toward the feet of the occupants.

As shown in FIGS. 1 and 2, the centrifugal blower 1 includes a motor 2, a first impeller 3 and a second impeller 5 that are rotationally driven around a rotation axis Ax extending in the axial direction by the motor 2, and a first impeller. It has a scroll housing 10 for accommodating the impeller 3 and the second impeller 5.

In the present specification, for convenience of explanation, the direction of the rotation axis Ax is referred to as an axial direction or a vertical direction. Further, the upper side and the lower side of FIGS. 1 and 2 are referred to as "one side in the axial direction" or "upper side in the axial direction" and "the other side in the axial direction" or "lower side in the axial direction", respectively. However, this does not mean that the direction of the rotation axis Ax coincides with the vertical direction when the air conditioner is actually incorporated in the vehicle. Further, in the present specification, unless otherwise specified, the direction of the radius of a circle drawn on a plane orthogonal to the rotation axis Ax about an arbitrary point on the rotation axis Ax is referred to as a radial direction. The circumferential direction of a circle is called the circumferential direction or the circumferential direction.

The first impeller 3 has a plurality of first blades 4 forming a first blade row arranged in the circumferential direction. The first impeller 3 is rotationally driven around the rotation axis Ax to blow out air in the space inside the radial direction of the first blade row toward the outside in the radial direction. Each of the first wings 4 has an inner edge 41 of the first wing facing inward in the radial direction, an outer edge 42 of the first wing facing outward in the radial direction, and one side of the first wing facing one side (upper side) in the axial direction. It has an edge 43 and a first wing other side edge 44 facing the other side (lower side) in the axial direction. When the first impeller 3 is rotationally driven, air is drawn into the first wing row in the region near the inner end edge 41 of the first wing of the first wing 4, and the drawn air is taken into the outer end of the first wing of the first wing 4. Extrude outward in the radial direction in the region near the edge 42.

The second impeller 5 is aligned with the first impeller 3 in the axial direction. The second impeller 5 has a plurality of second blades 6 forming a second blade row arranged in the circumferential direction. The second impeller 5 is rotationally driven around the rotation axis Ax to blow out air in the space inside the radial direction of the second blade row toward the outside in the radial direction. Each of the second wings 6 has an inner edge 61 of the second wing facing inward in the radial direction, an outer edge 62 of the second wing facing outward in the radial direction, and one side of the second wing facing one side (upper side) in the axial direction. It has an edge 63 and a second wing other side edge 64 facing the other side (lower side) in the axial direction. When the second impeller 5 is rotationally driven, air is drawn into the second wing row in the region near the inner end edge 61 of the second wing of the second wing 6, and the drawn air is taken into the outer end of the second wing of the second wing 6. Extrude outward in the radial direction in the region near the edge 62.

In the illustrated example, the axial dimension of the first wing 4 and the axial dimension of the second wing 6 are the same, but are not limited to this. The axial dimension of the first wing 4 and the axial dimension of the second wing 6 may be different.

A dividing member 7 is formed between the first blade row of the first impeller 3 and the second blade row of the second impeller 5. The dividing member 7 is formed in a circumferential shape along the blade row of the first impeller 3 and the second impeller 5. The dividing member 7 divides the space between the plurality of first wings 4 and the space between the plurality of second wings 6. In the example shown in FIGS. 1 to 3, the dividing member 7 is integrally formed with the first blade row of the first impeller 3 and the second blade row of the second impeller 5. The first blade row of the first impeller 3 is located on one side in the axial direction of the dividing member 7. Further, the second blade row of the second impeller 5 is located on the other side in the axial direction of the dividing member 7. The dividing member 7 has an inner end surface 75 of the dividing member facing inward in the radial direction and an outer end surface 76 of the dividing member facing outward in the radial direction.

Further, the inner deflection member 8 is integrally formed on the impellers 3 and 5. The inner deflection member 8 is a rotating body in a geometrical sense. In the illustrated example, it has a side peripheral portion 8a connected to the lower end of the second impeller 5 and a disk-shaped central portion 8b. The central portion 8b is connected to the rotating shaft 2a of the motor 2. The inner deflection member 8 forms an air flow passage between the inner deflection member 8 and the outlet side end portion 33 of the separation cylinder 30, which will be described later. The central portion 8b does not necessarily have to have a disk shape, and may have a well-known boss shape.

The scroll housing 10 has an internal space for accommodating the impellers 3 and 5, a suction port 11 that opens on one end side in the axial direction, and a discharge port 12 that opens in the circumferential direction. The discharge port 12 extends substantially in the tangential direction of the outer peripheral surface of the scroll housing 10 when the scroll housing 10 is viewed from the axial direction.

The internal space of the scroll housing 10 is divided (partitioned) by a circumferential partition wall 15 extending inward in the radial direction from the inner peripheral surface of the scroll housing 10. The partition wall 15 axially (s) the area between the inner peripheral surface of the scroll housing 10 and the outer peripheral surfaces of the impellers 3 and 5 and the internal space of the discharge port 12 in the internal space of the scroll housing 10. It is divided into upper and lower parts. Since the internal space of the scroll housing 10 is divided by the partition wall 15, the first air flow path 13 facing the first blade row of the first impeller 3 and the second impeller 5 are contained in the scroll housing 10. A second air flow path 14 facing the second blade row of the above is formed. The air flowing through the first air flow path 13 is sent out to the defroster outlet and / or the vent outlet of the vehicle. Further, the air flowing through the second air flow path 14 is sent out to the foot outlet of the vehicle.

In the illustrated example, the axial dimension of the first air flow path 13 and the axial dimension of the second air flow path 14 are the same, but are not limited to this. The axial dimension of the first air flow path 13 and the axial dimension of the second air flow path 14 may be different.

The partition wall 15 has a partition wall inner end surface 16 facing inward in the radial direction. The partition wall 15 is provided so as to be substantially at the same position as the dividing member 7 in the axial direction. In the illustrated example, the partition wall inner end surface 16 of the partition wall 15 faces the partition member outer end surface 76.

The separation cylinder 30 is inserted into the scroll housing 10 via the suction port 11. As can be understood by comparing and contrasting FIGS. 1 and 2, the cross section of the inlet side end (upper part) 31 of the separation cylinder 30 is approximately rectangular. The cross section of the central portion 32 of the separation cylinder 30 is circular or substantially circular. The cross-sectional shape of the separation cylinder 30 smoothly changes from a rectangular shape to a circular shape or a substantially circular shape as it approaches the central portion 32 from the inlet side end portion 31. The outlet side end (lower part) 33 of the separation cylinder 30 has a flare shape that increases in diameter as it approaches the lower end.

The entire separation cylinder 30 may be integrally molded by resin injection molding. Instead of this, the inlet side end portion (upper part) 31 of the separation cylinder 30 and the central portion 32 and the outlet side end portion (lower part) 33 of the separation cylinder 30 may be separately molded and then connected to each other. ..

The separation cylinder 30 extends axially through the inside of the suction port 11 in the radial direction and the inside of the first blade row of the first impeller 3 in the radial direction. The inlet side end portion 31 of the separation cylinder 30 is located on the outside of the scroll housing 10 (above the suction port 11 in the axial direction).

The separation cylinder 30 allows the flow of air sucked into the scroll housing 10 from the suction port 11 to pass through the first passage 30A outside the separation cylinder 30 and the second passage 30B inside the separation cylinder 30. Separates into a second air stream passing through. The first air flow flows into the radial inside of the first blade row of the first impeller 3 through the ring-shaped region outside the outer peripheral surface of the separation cylinder 30 in the suction port 11 of the scroll housing 10. The second air flow enters the inside of the separation cylinder 30 from the upper end of the separation cylinder 30 and flows into the inside of the second blade row of the second impeller 5 in the radial direction.

The outlet-side end 33 of the separation cylinder 30 diverts the inflowing first air flow outward in the radial direction, guides the inflowing first air flow to the first air flow path 13 through the first blade row of the first impeller 3, and flows in. The second air flow is turned outward in the radial direction and guided to the second air flow path 14 through the second blade row of the second impeller 5. More specifically, the outlet side end portion 33 has a first turning surface 34 facing one side (upper side) in the axial direction. The first turning surface 34 turns the first air flow outward in the radial direction. Further, the outlet side end portion 33 has a second turning surface 36 facing the other side (lower side) in the axial direction. The second turning surface 36 turns the second air flow outward in the radial direction.

As shown in FIGS. 1 and 2, an air intake housing 50 is arranged on one side (upper side) of the scroll housing 10 in the axial direction so as to cover the suction port 11. The scroll housing 10 and the air intake housing 50 may be integrally molded, or may be manufactured separately and then connected by a method such as screwing, bonding, or fitting. In a preferred embodiment, the separation cylinder 30 is a separate component from the scroll housing 10 and the air intake housing 50, and is supported at a predetermined position by the air intake housing 50.

The air intake housing 50 has a first opening 51, a second opening 52, a third opening 53, and a fourth opening 54. Inside air (vehicle interior air) can be introduced into the internal space of the air intake housing 50 from the vehicle interior space 55 (details are not shown) through the first opening 51 and the third opening 53. That is, the first opening 51 and the third opening 53 are the first and second inside air introduction ports for taking in the inside air into the air intake housing 50. Further, through the second opening 52 and the fourth opening 54, the outside air (from the outside of the vehicle) is introduced into the internal space of the air intake housing 50 from the outlet 56 (details are not shown) of the outside air introduction path provided in the vehicle. Incorporated air) can be introduced. That is, the second opening 52 and the fourth opening 54 are first and second outside air introduction ports for taking in outside air into the air intake housing 50.

By rotating the door 57 around the rotation shaft 57A, the inflow of air (inside air) from the first opening 51 into the air intake housing 50 can be allowed or blocked. By rotating the door 58 around the rotation shaft 58A, the inflow of air (outside air) from the second opening 52 into the air intake housing 50 can be allowed or blocked. By rotating the door 59 around the rotation shaft 59A to switch the position, air (inside air or outside air) flows into the air intake housing 50 through either the third opening 53 or the fourth opening 54. Can be made to.

Almost all of the air introduced into the air intake housing 50 from the first opening 51 and / or the second opening 52 passes through the first passage 30A, and from the third opening 53 and / or the fourth opening 54. The air intake housing 50 and the separation cylinder 30 are formed so that almost all of the air introduced into the air intake housing 50 passes through the second passage 30B.

The configuration of the air intake housing 50 is not limited to the configurations shown in FIGS. 1 and 2. For example, the

doors

57 and 58 of the air intake housing 50 may be rotary doors like the door 59.

A filter 80 is provided in the air intake housing 50. The filter 80 is arranged between the region where the first opening 51, the second opening 52, the third opening 53 and the fourth opening 54 are arranged and the inlet side end portion 31 of the separation cylinder 30, and is dust in the air. , Removes contaminants such as particles.

By the way, when the vehicle air conditioner is operated in the inside / outside air two-phase flow mode, high separability between the first air flow (outside air) and the second air flow (inside air) is required. This is due to the following reasons. That is, when the vehicle air conditioner is operated in the inside / outside air two-phase flow mode, dry outside air is applied to the windshield so as to prevent fogging of the windshield. However, if the outside air that hits the windshield is mixed with the moist inside air, the windshield anti-fog function of the vehicle air conditioner may be impaired. In particular, when the vehicle air conditioner is operated in the inside / outside air two-layer flow mode, the ventilation resistance of the second air flow path is higher than the ventilation resistance of the first air flow path depending on the position of the door in the vehicle air conditioner. It can be expensive. As a result, a part of the inside air flowing through the second air flow path may flow into the first air flow path through the gap between the elements constituting the centrifugal blower.

In consideration of such circumstances, the centrifugal blower 1 shown in FIGS. 1 to 3 is configured to suppress the possibility that the second air flow is mixed with the first air flow. More specifically, in the centrifugal blower 1 shown in FIGS. 1 to 3, there is a possibility that a part of the second air flow may enter the first air flow path 13 through the gap between the separation cylinder 30 and the dividing member 7. Is configured to suppress.

Specifically, the centrifugal blower 1 is configured as follows. That is, as is well shown in FIG. 3, the distance between the other side end portion 46 in the axial direction of the inner end edge 41 of the first blade and the radial outer edge portion 35 of the first turning surface 34 of the separation cylinder 30. D1 is larger than the distance D2 between the one-sided end portion 65 in the axial direction of the inner end edge 61 of the second blade and the edge portion 35 of the first turning surface 34 of the separation cylinder 30. In other words, the edge portion 35 of the first turning surface 34 is closer to the second wing 6 of the second impeller 5 than to the first wing 4 of the first impeller 3. As a result, when the impellers 3 and 5 are rotationally driven, the air in the vicinity of the edge 35 of the first turning surface 34 is drawn into the second blade row of the second impeller 5 and blown out from the second blade row. To. That is, a part of the first air flow flows into the second air flow path 14 through the gap between the outlet side end portion 33 of the separation cylinder 30 and the dividing member 7. As a result, the possibility that a part of the second air flow flows into the first air flow path 13 through the gap between the outlet side end portion 33 of the separation cylinder 30 and the dividing member 7 is suppressed.

In the example shown in FIG. 3, the edge portion 35 of the first turning surface 34 is located on the other side in the axial direction than the one side end portion 65 in the axial direction of the inner edge 61 of the second blade. As a result, the distance D1 between the other side end portion 46 of the first wing inner end edge 41 and the edge portion 35 of the first turning surface 34 is the one side end portion 65 of the second wing inner end edge 61 and the first turning surface. It is longer than the distance D2 from the edge 35 of 34.

Next, the operation of the vehicle air conditioner shown in FIGS. 1 to 3 will be described.

In the first operation mode (outside air mode) of the vehicle air conditioner, the second opening 52 and the fourth opening 54 are opened, and the first opening 51 and the third opening 53 are closed. This state is not shown. In this case, the outside air introduced from the second opening 52 forms a first air flow through the first passage 30A outside the separation cylinder 30. Further, the outside air introduced from the fourth opening 54 forms a second air flow passing through the second passage 30B inside the separation cylinder 30. Most of the air forming the first air flow is drawn into the first blade row by the first blade 4 of the first impeller 3 and pushed out into the first air flow path 13 by the first blade 4. On the other hand, a part of the air forming the first air flow (more specifically, the air flowing near the edge 35 of the separation cylinder 30) and the air forming the second air flow are the air of the second impeller 5. It is drawn into the second wing row by the second wing 6 and pushed out into the second air flow path 14 by the second wing 6.

In the second operation mode (inside / outside air two-phase flow mode), the second opening 52 and the third opening 53 are opened, and the first opening 51 and the fourth opening 54 are closed. This state is shown in FIGS. 1 and 2. In this case, the outside air FE introduced from the second opening 52 forms a first air flow through the first passage 30A outside the separation cylinder 30. Further, the inside air FR introduced from the third opening 53 forms a second air flow through the second passage 30B inside the separation cylinder 30. Most of the air forming the first air flow is drawn into the first blade row by the first blade 4 of the first impeller 3 and pushed out into the first air flow path 13 by the first blade 4. On the other hand, a part of the air forming the first air flow (more specifically, the air flowing near the edge 35 of the separation cylinder 30) and the air forming the second air flow are the air of the second impeller 5. It is drawn into the second wing row by the second wing 6 and pushed out into the second air flow path 14 by the second wing 6.

The second operation mode (inside / outside air two-phase flow mode) is used, for example, when operating in the differential foot mode. At this time, the harmonized air (air flowing through the first air flow path 13) having a relatively small amount of water is blown out from the defrost outlet of the vehicle interior toward the front glass (not shown) of the vehicle, and the relatively water content is relatively small. A large amount of harmonious air (air flowing through the second air flow path 14) is blown out from the foot outlet (not shown) of the passenger compartment toward the feet of the occupant.

In the third operation mode (inside air mode), the first opening 51 and the third opening 53 are opened, and the second opening 52 and the fourth opening 54 are closed. This state is not shown. In this case, the inside air introduced from the first opening 51 forms a first air flow through the first passage 30A outside the separation cylinder 30. Further, the inside air introduced from the third opening 53 forms a second air flow passing through the second passage 30B inside the separation cylinder 30. Most of the air forming the first air flow is drawn into the first blade row by the first blade 4 of the first impeller 3 and pushed out into the first air flow path 13 by the first blade 4. On the other hand, a part of the air forming the first air flow (more specifically, the air flowing near the edge 35 of the separation cylinder 30) and the air forming the second air flow are the air of the second impeller 5. It is drawn into the second wing row by the second wing 6 and pushed out into the second air flow path 14 by the second wing 6.

As described above, the air flowing through the second passage 30B flows into the second blade row of the second impeller 5. At this time, a part of the air flowing through the first passage 30A is drawn into the second blade row through the gap between the outlet side end portion 33 of the separation cylinder 30 and the dividing member 7, and thus one of the air flowing through the second passage 30B. It is suppressed that the portion flows into the first passage 30A or the first blade row of the first impeller 3 through the gap.

As described above, the centrifugal blower 1 of the first embodiment is a single suction type centrifugal blower 1 for a vehicle, and is a motor 2, a first impeller 3, a second impeller 5, and a split member. 7, a scroll housing 10, a partition wall 15, and a separation cylinder 30 are provided.

The first impeller 3 has a plurality of first blades 4 forming a circumferential first blade row. The first impeller 3 is rotationally driven by a motor 2 around a rotation axis Ax extending in the axial direction, and blows out air in the space inside the radial direction of the first blade row toward the outside in the radial direction.

The second impeller 5 has a plurality of second blades 6 forming a circumferential second blade row. The second impeller 5 is rotationally driven around the rotation axis Ax by the motor 2 to blow out air in the space inside the radial direction of the second blade row toward the outside in the radial direction.

The dividing member 7 is formed in a circumferential shape between the first wing row and the second wing row, and divides the space between the plurality of first wing 4 and the space between the plurality of second wing 6.

The scroll housing 10 has an internal space for accommodating the first impeller 3 and the second impeller 5, a suction port 11 that opens on one end side in the axial direction, and a discharge port 12 that opens in the circumferential direction.

The partition wall 15 covers an area between the inner peripheral surface of the scroll housing 10 and the outer peripheral surfaces of the first impeller 3 and the second impeller 5 in the internal space of the scroll housing 10, and the internal space of the discharge port 12. , The first air flow path 13 facing the first blade row and the second air flow path 14 facing the second blade row are formed by dividing in the axial direction.

The separation cylinder 30 extends axially through the inside of the suction port 11 in the radial direction and the inside of the first blade row in the radial direction. The separation cylinder 30 divides the air flow sucked into the scroll housing 10 from the suction port 11 into a first air flow passing through the outside of the separation cylinder 30 and a second air flow passing through the inside of the separation cylinder 30. It is provided as follows. Further, the separation cylinder 30 diverts the first air flow outward in the radial direction to guide it to the first air flow path 13, and also diverts the second air flow outward in the radial direction to guide the second air flow path 14 to the second air flow path 14. It has an exit side end 33 that guides the air.

The first blade row is located on one side of the dividing member 7 in the axial direction.

The second blade row is located on the other side of the split member 7 in the axial direction.

The outlet-side end 33 of the separation cylinder 30 has a first turning surface 34 that turns the first air flow outward in the radial direction, and a second turning surface 36 that turns the second air flow outward in the radial direction. Have.

The first wing 4 has a first wing inner edge 41 facing inward in the radial direction.

The second wing 6 has a second wing inner edge 61 facing inward in the radial direction.

The distance D1 between the other side end portion 46 in the axial direction of the inner end edge 41 of the first wing and the outer edge portion 35 in the radial direction of the first turning surface 34 is one side end in the axial direction of the inner end edge 61 of the second wing. The distance between the portion 65 and the radial outer edge portion 35 of the first turning surface 34 is longer than the distance D2.

According to such a centrifugal blower 1, the edge portion 35 of the first turning surface 34 is closer to the second blade 6 of the second impeller 5 than the first blade 4 of the first impeller 3. As a result, when the impellers 3 and 5 are rotationally driven, the air in the vicinity of the edge 35 of the first turning surface 34 is drawn into the second blade row of the second impeller 5 and blown out from the second blade row. To. That is, a part of the first air flow flows into the second air flow path 14 through the gap between the outlet side end portion 33 of the separation cylinder 30 and the dividing member 7. As a result, the possibility that a part of the second air flow flows into the first air flow path 13 through the gap is suppressed.

In particular, in the first embodiment, the radial outer edge portion 35 of the first turning surface 34 is located on the other side in the axial direction than the one side end portion 65 in the axial direction of the second blade inner end edge 61. is doing. As a result, the distance D1 becomes longer than the distance D2.

[Modified example of the first embodiment]

Next, with reference to FIG. 4, the centrifugal blower in the modified example of the first embodiment will be described.

FIG. 4 is a diagram corresponding to FIG. 3 and is a diagram for explaining a modification of the first embodiment. In the modification shown in FIG. 4, the same parts as those in the first embodiment shown in FIGS. 1 to 3 are designated by the same reference numerals, and detailed description thereof will be omitted.

In the modified example shown in FIG. 4, the split member 7 projects axially from one side surface (upper surface) of the main body 70 at the main body 70 extending in the radial direction and the radial inner end 71 of the main body 70. It has an inner one-side protruding portion 72. The inner edge 41 of the first wing is connected to the inner one-side protrusion 72. Since the dividing member 7 has an inner one-side protruding portion 72 connected to the first wing inner end edge 41, the position of the other side end portion 46 of the first wing inner end edge 41 in the axial direction can be determined by the dividing member 7. It can be determined without depending on the position of the main body 70 of 7 in the axial direction. Therefore, it is easy to increase the distance D1 between the other side end portion 46 of the first blade inner end edge 41 and the edge portion 35 of the first turning surface 34. Further, since the dividing member 7 has the inner one-side protruding portion 72, the range in the axial direction in which the separation cylinder 30 can be arranged with respect to the dividing member 7 is expanded so that the distance D1 is longer than the distance D2. do. As a result, when assembling the centrifugal blower 1, the separation cylinder 30 is arranged with respect to the dividing member 7 so that the distance D1 is longer than the distance D2 even if there is a dimensional tolerance of each component constituting the centrifugal blower 1. Is easy. Therefore, as shown in FIG. 4, even if the separation cylinder 30 is arranged with respect to the division member 7 so that the outlet side end portion 33 of the separation cylinder 30 and the main body portion 70 of the division member 7 face each other, the distance D1 is set. It can be longer than the distance D2.

As shown in FIG. 4, the split member 7 may further have an inner other side protruding portion 73 that protrudes in the axial direction from the other side surface of the main body portion 70 at the end portion 71. In the example shown in FIG. 4, the inner other side protrusion 73 is connected to the inner edge 61 of the second blade. Also in this case, if the distance D1 is longer than the distance D2, a part of the second air flow flows into the first air flow path 13 through the gap between the outlet side end portion 33 of the separation cylinder 30 and the dividing member 7. The fear is suppressed. In addition, since the inner other side protruding portion 73 connected to the inner edge 61 of the second wing is provided, the first air flow passing through the first passage 30A unintentionally passes through the second passage 30B. It is possible to suppress the inflow to the flow.

[Second Embodiment]

Next, the centrifugal blower according to the second embodiment will be described with reference to FIG.

FIG. 5 is a diagram corresponding to FIG. 3 and is a diagram for explaining a second embodiment. In the second embodiment shown in FIG. 5, the same parts as those in the first embodiment shown in FIGS. 1 to 3 are designated by the same reference numerals, and detailed description thereof will be omitted.

In the example shown in FIG. 5, the length of the other side edge 44 of the first wing 4 is shorter than the length of the one side edge 63 of the second wing 6. As a result, the other side end portion 46 of the first wing inner end edge 41 is located radially outside the one side end portion 65 of the second wing inner end edge 61.

Since the other side end portion 46 of the first wing inner end edge 41 is located radially outside the one side end portion 65 of the second wing inner end edge 61, the other side of the first wing inner end edge 41 It is easy to increase the distance D1 between the end portion 46 and the edge portion 35 of the first turning surface 34. That is, as shown in FIG. 5, even if the outlet side end portion 33 of the separation cylinder 30 faces the inner end surface 75 of the dividing member, the distance D1 can be made longer than the distance D2. This means that the axial range in which the separation cylinder 30 can be arranged with respect to the dividing member 7 is expanded so that the distance D1 is longer than the distance D2. Therefore, when assembling the centrifugal blower 1, the separation cylinder 30 is arranged with respect to the dividing member 7 so that the distance D1 is longer than the distance D2 even if there is a dimensional tolerance of each component constituting the centrifugal blower 1. Is easy.

In the illustrated example, the axial position of the edge 35 of the first turning surface 34 is the same as the axial position of the other side end 46 of the inner edge 41 of the first wing, but the distance D1 is the distance D2. Longer than.

Of course, in the example shown in FIG. 5, the axial position of the edge portion 35 of the first turning surface 34 is the other side (in the axial direction) than the axial position of the other side end portion 46 of the first blade inner end edge 41. It may be located on the lower side).

Further, in the example shown in FIG. 5, the inner end surface 75 of the dividing member is connected to the inner end edge 61 of the second blade, but the present invention is not limited to this. For example, as shown in FIG. 6, the dividing member inner end surface 75 may be formed at the same position as the first blade inner end edge 41 in the radial direction.

[Third Embodiment]

Next, the centrifugal blower according to the third embodiment will be described with reference to FIG. 7.

FIG. 7 is a diagram corresponding to FIG. 3 and is a diagram for explaining a third embodiment. In the third embodiment shown in FIG. 7, the same parts as those in the first embodiment shown in FIGS. 1 to 3 are designated by the same reference numerals, and detailed description thereof will be omitted.

In the example shown in FIG. 7, the dividing member 7 becomes thicker toward the outside in the radial direction. The axial dimension L1 of the split member outer end face 76 is longer than the axial dimension L2 of the split member inner end face 75. Since the dimension L1 of the dividing member 7 is longer than the dimension L2, it is easy to make the outer end surface 76 of the dividing member and the inner end surface 16 of the partition wall 15 face each other. That is, the range in the axial direction in which the impellers 3 and 4 can be arranged with respect to the partition wall 15 is expanded so that the outer end surface 76 of the dividing member and the inner end surface 16 of the partition wall 15 face each other. As a result, when assembling the centrifugal blower 1, the impeller so that the outer end surface 76 of the dividing member and the inner end surface 16 of the partition wall 15 face each other even if there is a dimensional tolerance of each component constituting the centrifugal blower 1. It is easy to arrange the 3 and 4 with respect to the partition wall 15. Since the outer end surface 76 of the dividing member and the inner end surface 16 of the partition wall face each other, a part of the air blown out from the second blade row of the impeller 5 in the centrifugal direction flows into the first air flow path 13. , Is suppressed.

In the example shown in FIG. 7, the dimension L1 is longer than the dimension L2 because the dividing member 7 becomes thicker toward the outside in the radial direction, but the present invention is not limited to this. For example, the dimension L1 may be longer than the dimension L2 by making the shape of the split member 7 as shown in FIG.

In the example shown in FIG. 8, the split member 7 has a main body portion 70 extending in the radial direction and an outer end portion 77 on the radial outer side of the main body portion 70, which protrudes axially from one side surface (upper surface) of the main body portion 70. It has a one-side projecting portion 78 and an outer other-side projecting portion 79 projecting axially from the other side surface (lower surface) of the main body portion 70. The outer edge 42 of the first wing is connected to the outer one-side protrusion 78. Further, the outer edge 62 of the second wing is connected to the outer other side protrusion 79. By providing the split member 7 with the outer one-side protruding portion 78 and / or the outer other-side protruding portion 79 in this way, the dimension L1 of the split member 7 may be longer than the dimension L2.

In the example shown in FIG. 8, the split member 7 further has an inner one-side projecting portion 72 projecting axially from one side surface of the main body 70 at the radial inner end 71 of the main body 70, and the end portion. The 71 has an inner other side protruding portion 73 that protrudes in the axial direction from the other side surface of the main body portion 70. The inner edge 41 of the first wing is connected to the inner one-side protrusion 72. Further, the inner end edge 61 of the second wing is connected to the inner other side protruding portion 73. Even with such a split member 7, if the dimension L1 is longer than the dimension L2, the same effect as that of the centrifugal blower 1 shown in FIG. 7 can be obtained. Further, since the split member 7 is provided with the inner one-side protruding portion 72, the same effect as that of the centrifugal blower 1 shown in FIG. 4 can be obtained. Further, since the split member 7 is provided with the inner side protruding portion 73, the same effect as that of the centrifugal blower 1 shown in FIG. 4 can be obtained.

[Fourth Embodiment]

Next, the centrifugal blower according to the fourth embodiment will be described with reference to FIG. 9.

FIG. 9 is a diagram corresponding to FIG. 3 and is a diagram for explaining a fourth embodiment. In the fourth embodiment shown in FIG. 9, the same parts as those in the first embodiment shown in FIGS. 1 to 3 are designated by the same reference numerals, and detailed description thereof will be omitted.

In the example shown in FIG. 9, the dividing member 7 is located on the other side (lower side) in the axial direction with respect to the partition wall 15. The other end portion 48 in the axial direction of the outer edge 42 of the first wing of the first wing 4 is located on the other side in the axial direction with respect to the inner end surface 16 of the partition wall of the partition wall 15. The air drawn into the first blade row of the first impeller 3 by the other side end portion 48 of the first blade outer end edge 42 located on the other side in the axial direction with respect to the partition wall inner end surface 16. Is blown out to the second air flow path 14. As a result, the possibility that the inside air blown out from the second impeller 5 flows into the first air flow path 13 through the gap between the partition wall 15 and the dividing member 7 is suppressed.

In the example shown in FIG. 9, since the dividing member 7 is located on the other side (lower side) in the axial direction with respect to the partition wall 15, the other side end portion 48 of the first wing outer edge 42 is partitioned. It is located on the other side in the axial direction with respect to the inner end surface 16 of the partition wall of the wall 15, but is not limited to this. For example, by forming the dividing member 7 as shown in FIG. 10, the other side end portion 48 of the first blade outer edge 42 is located on the other side in the axial direction with respect to the partition wall inner end surface 16 of the partition wall 15. May be.

In the example shown in FIG. 10, the dividing member 7 is inclined toward the other side (lower side) in the axial direction as it goes outward in the radial direction. As a result, the other side end portion 48 of the first wing outer end edge 42 of the first wing 4 is located on the other side in the axial direction with respect to the partition wall inner end surface 16. In this case as well, the same effect as that of the centrifugal blower 1 shown in FIG. 9 can be obtained.

[Fifth Embodiment]

Next, the centrifugal blower according to the fifth embodiment will be described with reference to FIG.

FIG. 11 is a diagram corresponding to FIG. 9 and is a diagram for explaining a fifth embodiment. In the fifth embodiment shown in FIG. 11, the same parts as those in the fourth embodiment shown in FIG. 9 are designated by the same reference numerals, and detailed description thereof will be omitted.

In the example shown in FIG. 11, the dividing member 7 extends to the other side (lower side) of the partition wall 15 in the axial direction. The outer end surface 76 of the dividing member is located on the outer side in the radial direction and on the other side (lower side) in the axial direction of the partition wall 15 than the inner end surface 16 of the partition wall. Since the outer end surface 76 of the dividing member is located on the other side in the axial direction of the partition wall 15, a part of the air drawn into the first blade row of the first impeller 3 is separated into the second air flow path 14. It is blown out to. As a result, the possibility that the inside air blown out from the second impeller 5 flows into the first air flow path 13 through the gap between the partition wall 15 and the dividing member 7 is suppressed. Further, when the dividing member 7 extends to the other side (lower side) of the partition wall 15 in the axial direction and the outer end surface 76 of the dividing member is located radially outside the inner end surface 16 of the partition wall, the second part is formed. The possibility that the inside air blown out from the impeller 5 flows into the first air flow path 13 through the gap between the partition wall 15 and the dividing member 7 is more effectively suppressed.

[Sixth Embodiment]

Next, the centrifugal blower according to the sixth embodiment will be described with reference to FIG. 12.

FIG. 12 is a diagram corresponding to FIG. 8 and is a diagram for explaining the sixth embodiment. In the sixth embodiment shown in FIG. 12, the same parts as those of the modified example of the third embodiment shown in FIG. 8 are designated by the same reference numerals, and detailed description thereof will be omitted.

In the example shown in FIG. 12, the outlet side end portion 33 is bifurcated. More specifically, the outlet side end portion 33 has a first turning portion 33a extending from the central portion 32 of the separation cylinder 30, and a first turning portion 33a extending from the central portion 32 to the other side (lower side) in the axial direction of the first turning portion 33a. It has two turning portions 33b. The surface of the first turning portion 33a facing one side (upper side) in the axial direction forms the first turning surface 34. Further, the surface of the second turning portion 33b facing the other side (lower side) in the axial direction forms the second turning surface 36. Even when the separation cylinder 30 has such a shape, if the distance D1 is longer than the distance D2, a part of the second air flow is a gap between the outlet side end portion 33 of the separation cylinder 30 and the dividing member 7. The possibility of flowing into the first air flow path 13 through the air flow path 13 is suppressed.

Further, the outlet side end portion 33 of the separation cylinder 30 has a first turning portion 33a and a second turning portion 33b located on the other side in the axial direction of the first turning portion 33a, so that the outlet side end portion At 33, the air flowing through the second passage 30B can be axially separated from the air flowing through the first passage 30A. As a result, the possibility that the air flowing through the second passage 30B is drawn into the first blade row of the first impeller 3 and flows into the first air flow path 13 is effectively suppressed.

In the above-described embodiment and its modification, when the first turning portion 33a of the outlet side end portion 33 or the outlet side end portion 33 of the separation cylinder 30 is rounded as shown in FIG. 13, the first turning The edge portion 35 of the surface 34 shall indicate the next position. That is, the edge portion 35 of the first turning surface 34 is a position where the surface S1 extending from the first turning surface 34 and the surface S2 in contact with the outlet side end portion 33 extending in parallel with the axial direction intersect. Point to.

In addition, although some modifications to the above-described embodiments have been described above, it is naturally possible to apply a plurality of modifications in combination as appropriate.

Since the centrifugal blower for a vehicle according to the present invention can be industrially manufactured and can be the subject of commercial transactions, it can be industrially used with economic value.

1 Centrifugal blower

2 motor

3 1st impeller

4 1st wing

5 Second impeller

6 Second wing

7 Dividing member

10 Scroll housing

13 First air flow path

14 Second air flow path

15 partition wall

30 Separation cylinder

34 First turning surface

36 Second turning surface

50 Air intake housing

Ax rotation axis

Claims

It is a one-suction type centrifugal blower (1) for vehicles.

Motor (2) and

It has a plurality of first blades (4) forming the first blade row in the circumferential direction, and is rotationally driven by the motor (2) around a rotation axis (Ax) extending in the axial direction, and the radius of the first blade row. The first impeller (3), which blows out the air in the space inside the direction toward the outside in the radial direction,

It has a plurality of second blades (6) forming a circumferential second blade row, and is rotationally driven by the motor (2) around the rotation axis (Ax) to be inside the radial direction of the second blade row. The second impeller (5), which blows out the air in the space toward the outside in the radial direction,

A circumferential space is formed between the first wing row and the second wing row, and the space between the plurality of first wing (4) and the space between the plurality of second wing (6) are formed. The dividing member (7) to be divided and

An internal space for accommodating the first impeller (3) and the second impeller (5), a suction port (11) opening on one end side in the axial direction, and a discharge port (12) opening in the circumferential direction. And a scroll housing (10) with

A region of the internal space of the scroll housing (10) between the inner peripheral surface of the scroll housing (10) and the outer peripheral surfaces of the first impeller (3) and the second impeller (4). Further, the internal space of the discharge port (12) is divided in the axial direction, and the first air flow path (13) facing the first blade row and the second air flow path facing the second blade row are divided. The partition wall (15) forming the (14) and

A separation cylinder (30) extending in the axial direction through the radial inside of the suction port (11) and the radial inside of the first blade row, and the scroll housing (10) from the suction port (11). The flow of air sucked into the inside is provided so as to be divided into a first air flow passing through the outside of the separation cylinder (30) and a second air flow passing through the inside of the separation cylinder (30). The first air flow is turned outward in the radial direction to be guided to the first air flow path (13), and the second air flow is turned outward in the radial direction to be guided to the second air flow path (14). ), With a separation tube (30) having an outlet side end (33).

The first blade row is located on one side of the dividing member (7) in the axial direction.

The second blade row is located on the other side of the dividing member (7) in the axial direction.

The outlet side end portion (33) of the separation cylinder (30) has a first turning surface (34) that diverts the first air flow outward in the radial direction and a second air flow outside the radial direction. It has a second turning surface (36) that turns in the direction, and has.

The first wing (4) has a first wing inner edge (41) facing inward in the radial direction.

The second wing (6) has a second wing inner edge (61) facing inward in the radial direction.

The distance (D1) between the other side end portion (46) of the first blade inner end edge (41) in the axial direction and the radial outer edge portion (35) of the first turning surface (34) is More than the distance (D2) between the one side end portion (65) of the second wing inner end edge (61) in the axial direction and the radial outer edge portion (35) of the first turning surface (34). Long, centrifugal blower (1).
The radial outer edge (35) of the first turning surface (34) is more axial than the axial one-sided end (65) of the second wing inner edge (61). The centrifugal blower (1) according to claim 1, which is located on the other side.
The split member (7) has a main body portion (70) extending in the radial direction and an end portion (71) on the inner side in the radial direction of the main body portion (70) from one side surface of the main body portion (70). It has an inner one-sided protrusion (72) that protrudes in the axial direction, and has.

The centrifugal blower (1) according to claim 1 or 2, wherein the first blade inner edge (41) is connected to the inner one-side protrusion (72).
The split member (7) has a main body portion (70) extending in the radial direction and an end portion (71) on the inner side in the radial direction of the main body portion (70) from the other side surface of the main body portion (70). It has an inner other side protrusion (73) that protrudes in the axial direction, and has.

The centrifugal blower (1) according to any one of claims 1 to 3, wherein the second blade inner edge (61) is connected to the inner other side protrusion (73).
The other side end portion (46) of the first wing inner end edge (41) in the axial direction has a radius higher than that of the one side end portion (65) of the second wing inner end edge (61) in the axial direction. The centrifugal blower (1) according to any one of claims 1 to 4, which is located outside the direction.
The axial position of the radial outer edge portion (35) of the first turning surface (34) is the axial direction of the other side end portion (46) of the first blade inner end edge (41) in the axial direction. The centrifugal blower (1) according to claim 5, which is located at the same position as the position or on the other side in the axial direction from the position.
The axial dimension (L1) of the split member outer end face (76) facing the radial outer side of the split member (7) is the radial inner end face (75) of the split member (7). The centrifugal blower (1) according to any one of claims 1 to 6, which is longer than the axial dimension (L2) of).
The first wing (4) has a first wing outer edge (42) facing outward in the radial direction.

The other side end portion (48) of the first blade outer edge (42) in the axial direction is axially more than the inner end surface (16) of the partition wall facing inward in the radial direction of the partition wall (15). The centrifugal blower (1) according to any one of claims 1 to 7, which is located on the other side.
The outer end face (76) of the split member facing the radial outer side of the split member (7) is radially outside and more than the inner end face (16) of the partition wall facing the radial inner side of the partition wall (15). The centrifugal blower (1) according to any one of claims 1 to 8, which is located on the other side of the partition wall (15) in the axial direction.