BLOWER DEVICE

Description

CROSS REFERENCE TO RELATED APPLICATIONS

This application is a continuation application of International Patent Application No. PCT/JP2024/012018 filed on Mar. 26, 2024, which designated the U.S. and claims the benefit of priority from Japanese Patent Application No. 2023-060325 filed on Apr. 3, 2023. The entire disclosures of all of the above applications are incorporated herein by reference.

TECHNICAL FIELD

The present disclosure relates to a blower device.

BACKGROUND

A previously proposed blower device includes: a blower fan, which is disposed in an air passage in an air conditioning case; and a plurality of swirl flow suppressors that are provided in the air passage to allow an airflow blown from the blower fan to pass through. The blower fan draws in the air from one side in an axial direction and blows the air out toward a radially outer side about an axis of the blower fan by rotating about the axis.

SUMMARY

This section provides a general summary of the disclosure, and is not a comprehensive disclosure of its full scope or all of its features.

According to the present disclosure, there is provided a blower device that may include an air conditioning case, a blower fan, a cover and at least one swirl flow suppressor. The air conditioning case may have an inner wall. The inner wall may form an air passage which is configured to conduct air. The blower fan may be disposed in the air passage. A direction, in which an axis of the blower fan extends, is defined as an axial direction. The blower fan may be configured to rotate about the axis to draw in the air from one side in the axial direction and to blow the air out toward a radially outer side in a radial direction about the axis. The cover may be disposed on another side in the axial direction with respect to the blower fan in the air passage and may be formed to cover the blower fan from the another side in the axial direction. The cover may form, between the cover and the inner wall, a through-passage that may be configured to conduct the air blown out from the blower fan toward the another side in the axial direction. The at least one swirl flow suppressor may be disposed in the through-passage and may be elongated along the radial direction. The at least one swirl flow suppressor may be configured to suppress a swirl flow of the air generated by rotation of the blower fan, and thereby to generate an airflow that flows toward the another side in the axial direction. One-side end portion of the at least one swirl flow suppressor, which faces the one side in the axial direction, may be formed to extend toward the another side in the axial direction as the one-side end portion extends from a radially inner side toward the radially outer side in the radial direction.

BRIEF DESCRIPTION OF DRAWINGS

The drawings described herein are for illustrative purposes only of selected embodiments and not all possible implementations, and are not intended to limit the scope of the present disclosure.

FIG. 1 is a cross-sectional view showing a configuration of a vehicle air-conditioning unit according to a first embodiment and being taken along a virtual plane parallel to an up-down direction of the vehicle and including a fan axis, the view being provided to assist in explaining an arrangement relationship among an air-conditioning case, a blower and a flow straightener mechanism.

FIG. 2 is a cross-sectional view taken along line II-II in FIG. 1, the view being provided to assist in explaining a plurality of swirl flow suppressors and a cover, which constitute the flow straightener mechanism in the first embodiment.

FIG. 3 is a cross-sectional view showing a blower fan and the flow straightener mechanism according to the first embodiment shown in FIG. 1 and being taken along a virtual plane including the fan axis, the view being provided to assist in explaining the plurality of swirl flow suppressors and the cover that constitute the flow straightener mechanism.

FIG. 4 is a view for assisting in explaining the plurality of swirl flow suppressors that constitute the flow straightener mechanism according to the first embodiment shown in FIG. 1, the view showing a state in which the flow straightener mechanism is optically projected by a light source from one side in its axial direction.

FIG. 5 is a cross-sectional view showing a blower fan and a flow straightener mechanism according to a second embodiment and being taken along a virtual plane including a fan axis, the view being provided to assist in explaining a plurality of swirl flow suppressors and a cover that constitute the flow straightener mechanism.

FIG. 6 is a cross-sectional view corresponding to FIG. 2 and showing a flow straightener mechanism according to a third embodiment and being taken along a virtual plane perpendicular to a fan axis, the view being provided to assist in explaining a plurality of swirl flow suppressors and a cover.

FIG. 7 is a cross-sectional view taken along line VII-VII in FIG. 6, the view being provided to assist in explaining a front-side guide and a rear-side guide that constitute the swirl flow suppressor.

FIG. 8 is a cross-sectional view taken along line VIII-VIII in FIG. 6, the view being provided to assist in explaining the front-side guide and the rear-side guide that constitute the swirl flow suppressor.

FIG. 9 is a cross-sectional view taken along line IX-IX in FIG. 6, the view being provided to assist in explaining the front-side guide and the rear-side guide that constitute the swirl flow suppressor.

FIG. 10 is a view provided to assist in explaining an acute angle defined between an end surface shown in FIG. 7 and a virtual plane.

FIG. 11 is a view provided to assist in explaining an acute angle defined between the end surface shown in FIG. 8 and a virtual plane.

FIG. 12 is a view provided to assist in explaining an acute angle defined between the end surface shown in FIG. 9 and a virtual plane.

FIG. 13 is a cross-sectional view showing a flow straightener mechanism according to a fourth embodiment and being taken along a virtual plane including the fan axis, the view being provided to assist in explaining a plurality of swirl flow suppressors and a cover that constitute the flow straightener mechanism.

FIG. 14 is a cross-sectional view taken along line XIV-XIV in FIG. 13, the view being provided to assist in explaining a dimension of the swirl flow suppressor measured in a rotational direction.

FIG. 15 is a cross-sectional view taken along line XV-XV in FIG. 13, the view being provided to assist in explaining a dimension of the swirl flow suppressor measured in the rotational direction.

FIG. 16 is a cross-sectional view taken along line XVI-XVI in FIG. 13, the view being provided to assist in explaining a dimension of the swirl flow suppressor measured in the rotational direction.

FIG. 17 is a cross-sectional view showing a flow straightener mechanism according to a fifth embodiment and being taken along a virtual plane including the fan axis, the view being provided to assist in explaining a plurality of swirl flow suppressors and a cover that constitute the flow straightener mechanism.

FIG. 18 is a cross-sectional view showing a flow straightener mechanism according to a sixth embodiment and being taken along a virtual plane including the fan axis, the view being provided to assist in explaining a plurality of swirl flow suppressors, a reinforcing ring and a cover that constitute the flow straightener mechanism.

FIG. 19 is a cross-sectional view showing one swirl flow suppressor among a plurality of swirl flow suppressors, which constitute a flow straightener mechanism according to a seventh embodiment, the view being taken along a virtual plane parallel to both the rotational direction and a fan axial direction and being provided to assist in explaining a shape of the swirl flow suppressor.

FIG. 20 is a cross-sectional view showing a flow straightener mechanism according to an eighth embodiment and being taken along a virtual plane parallel to both the fan axial direction and a radial direction, the view being provided to assist in explaining the shape of the swirl flow suppressor.

FIG. 21 is a cross-sectional view showing part of a flow straightener mechanism according to an eighth embodiment and being taken along a virtual plane including the fan axis, the view being provided to assist in explaining a flow velocity of an airflow that has passed through the swirl flow suppressor and an airflow flowing from a radially outer side toward a radially inner side.

FIG. 22 is a cross-sectional view showing part of a flow straightener mechanism in a comparative example of the eighth embodiment and being taken along a virtual plane including the fan axis, the view being provided to assist in explaining a flow velocity of an airflow that has passed through the swirl flow suppressor and an airflow flowing from the radially outer side toward the radially inner side.

FIG. 23 is a cross-sectional view showing a flow straightener mechanism according to a ninth embodiment and being taken along a virtual plane parallel to both the fan axial direction and the radial direction, the view being provided to assist in explaining a shape of a swirl flow suppressor.

FIG. 24 is a cross-sectional view showing a flow straightener mechanism according to a tenth embodiment and being taken along a virtual plane including the fan axis, the view being provided to assist in explaining a plurality of swirl flow suppressors and a cover that constitute the flow straightener mechanism.

FIG. 25 is a cross-sectional view showing a flow straightener mechanism according to an eleventh embodiment and being taken along a virtual plane including the fan axis, the view being provided to assist in explaining a plurality of swirl flow suppressors and a cover that constitute the flow straightener mechanism.

FIG. 26 is a cross-sectional view showing a flow straightener mechanism according to a twelfth embodiment and being taken along a virtual plane including the fan axis, the view being provided to assist in explaining a plurality of swirl flow suppressors and a cover that constitute the flow straightener mechanism.

FIG. 27 is a cross-sectional view taken along line XXVII-XXVII in FIG. 26 according to the twelfth embodiment, the view being provided to assist in explaining a dimension of the swirl flow suppressor measured in the rotational direction.

FIG. 28 is a cross-sectional view taken along line XXVIII-XXVIII in FIG. 26 according to the twelfth embodiment, the view being provided to assist in explaining a dimension of the swirl flow suppressor measured in the rotational direction.

FIG. 29 is a cross-sectional view taken along line XXIX-XXIX in FIG. 26 according to the twelfth embodiment, the view being provided to assist in explaining a dimension of the swirl flow suppressor measured in the rotational direction.

FIG. 30 is a perspective view of one swirl flow suppressor among a plurality of swirl flow suppressors according to a thirteenth embodiment, viewed from the other side in the rotational direction, the view being provided to assist in explaining the swirl flow suppressor formed in a forwardly extending shape and a forwardly inclined shape, with a dotted line indicates a comparative example of the swirl flow suppressor.

FIG. 31 is a perspective view provided to assist in explaining the swirl flow suppressor according to the thirteenth embodiment, with a dotted line indicating a comparative example of the swirl flow suppressor.

FIG. 32 is a perspective view of one single swirl flow suppressor among a plurality of swirl flow suppressors according to a fourteenth embodiment, viewed from the other side in the rotational direction, the view being provided to assist in explaining the swirl flow suppressor formed in a backwardly extending shape and a forwardly inclined shape, with a dashed line indicating a comparative example of the swirl flow suppressor.

FIG. 33 is a perspective view provided to assist in explaining the swirl flow suppressor according to the fourteenth embodiment, with a dashed line indicating a comparative example of the swirl flow suppressor.

FIG. 34 is a perspective view of one single swirl flow suppressor among a plurality of swirl flow suppressors according to a fifteenth embodiment, viewed from the other side in the rotational direction, the view being provided to assist in explaining the swirl flow suppressor having a backward shape and a forward-tilted shape, with a dashed line indicating a comparative example of the swirl flow suppressor.

FIG. 35 is a perspective view provided to assist in explaining the swirl flow suppressor according to the fifteenth embodiment, with a dashed line indicating a comparative example of the swirl flow suppressor.

FIG. 36 is a perspective view of one swirl flow suppressor among a plurality of swirl flow suppressors according to a sixteenth embodiment, viewed from the other side in the rotational direction, the view being provided to assist in explaining the swirl flow suppressor having a backward shape and a forward-tilted shape, with a dashed line indicating a comparative example of the swirl flow suppressor.

FIG. 37 is a perspective view provided to assist in explaining the swirl flow suppressor according to the sixteenth embodiment, with a dashed line indicating a comparative example of the swirl flow suppressor.

DETAILED DESCRIPTION

A previously proposed blower device includes: a blower fan, which is disposed in an air passage in an air conditioning case; and a plurality of swirl flow suppressors that are provided in the air passage to allow an airflow blown from the blower fan to pass through. The blower fan draws in the air from one side in an axial direction and blows the air out toward a radially outer side about an axis of the blower fan by rotating about the axis.

The swirl flow suppressors are disposed on the other side of the blower fan in the axial direction and form an air passage that allows the air blown from the blower fan to pass toward the other side in the axial direction. The swirl flow suppressor suppresses a swirl flow generated by the rotation of the blower fan.

Accordingly, it is possible to avoid unevenness in the amount of the blown airflow caused by the swirl flow generated by the rotation of the blower fan. Therefore, it is not necessary to excessively restrict the arrangement of the air outlet in order to avoid the unevenness in the amount of the blown airflow.

The swirl flow suppressors of the previously proposed blower device suppress the swirl flow of the airflow blown from the blower fan. However, according to the study of the inventors of the present application, since the high-speed swirl flow blown from the blower fan collides on the swirl flow suppressors, noise is generated due to the collision.

Further, according to the study of the inventors of the present application, in a case where a cover, which covers the blower fan from the other side in the axial direction, is provided to the swirl flow suppressors, an air flow passage is formed on a radially outer side of the cover.

In this case, a cross-sectional area of a cross section of the airflow passage becomes smaller than a cross-sectional area of a cross section of a downstream-side air flow passage, which is located on a downstream side of the swirl flow suppressors in the air conditioning case.

Here, when a direction, in which a main stream of the airflow flows in the air flow passage, is defined as a main flow direction, the cross section of the air flow passage refers to a cross section obtained by cutting the air flow passage along a virtual plane that is perpendicular to the main flow direction.

Accordingly, since the air flows at the high speed toward the other side in the axial direction through the air passage, which is formed by the swirl flow suppressors and has the small cross-sectional area, a large pressure loss occurs, and noise is generated.

According to one aspect of the present disclosure, there is provided a blower device that includes:

• • an air conditioning case that has an inner wall, wherein the inner wall forms an air passage which is configured to conduct air;
  • a blower fan that is disposed in the air passage, wherein a direction, in which an axis of the blower fan extends, is defined as an axial direction, and the blower fan is configured to rotate about the axis to draw in the air from one side in the axial direction and to blow the air out toward a radially outer side in a radial direction about the axis;
  • a cover that is disposed on another side in the axial direction with respect to the blower fan in the air passage and is formed to cover the blower fan from the another side in the axial direction, wherein the cover forms, between the cover and the inner wall, a through-passage that is configured to conduct the air blown out from the blower fan toward the another side in the axial direction; and
  • at least one swirl flow suppressor that is disposed in the through-passage and is elongated along the radial direction, wherein the at least one swirl flow suppressor is configured to suppress a swirl flow of the air generated by rotation of the blower fan, and thereby to generate an airflow that flows toward the another side in the axial direction, wherein:
  • a one-side end portion of the at least one swirl flow suppressor, which faces the one side in the axial direction, is formed to extend toward the another side in the axial direction as the one-side end portion extends from a radially inner side toward the radially outer side in the radial direction.

According to this aspect, when the swirl flow collides with the at least one swirl flow suppressor, the flow velocity of the air is reduced in comparison to a case where the at least one swirl flow suppressor is formed to extend from the radially inner side toward the radially outer side. This makes it possible to reduce noise generated when the swirl flow collides with the at least one swirl flow suppressor.

Accordingly, it is possible to provide the blower device configured to reduce the noise.

Furthermore, according to another aspect, there is provided a blower device that includes:

• • an air conditioning case that has an inner wall, wherein the inner wall forms an air passage which is configured to conduct air;
  • a blower fan that is disposed in the air passage, wherein a direction, in which an axis of the blower fan extends, is defined as an axial direction, and the blower fan is configured to rotate about the axis to draw in the air from one side in the axial direction and to blow the air out toward a radially outer side in a radial direction about the axis;
  • a cover that is disposed on another side in the axial direction with respect to the blower fan in the air passage and is formed to cover the blower fan from the another side in the axial direction, wherein the cover forms, between the cover and the inner wall, a through-passage that is configured to conduct the air blown out from the blower fan toward the another side in the axial direction; and
  • at least one swirl flow suppressor that is disposed in the through-passage and is elongated along the radial direction, wherein the at least one swirl flow suppressor is configured to suppress a swirl flow of the air generated by rotation of the blower fan, and thereby to generate an airflow that flows toward the another side in the axial direction, wherein:
  • a one-side end portion of the at least one swirl flow suppressor, which faces the one side in the axial direction, is formed to extend toward the one side in the axial direction as the one-side end portion extends from a radially inner side toward the radially outer side in the radial direction.

According to this aspect, the at least one swirl flow suppressor can generate the airflow, in which the flow velocity of the air increases from the radially inner side toward the radially outer side in the radial direction.

Furthermore, according to this aspect, it is possible to increase a difference between a flow velocity of the air on the radially inner side and a flow velocity of the air on the radially outer side in a flow velocity distribution of the airflow that has passed through the at least one swirl flow suppressor, as compared to a case where the at least one swirl flow suppressor is formed to extend from the radially inner side toward the radially outer side.

Accordingly, on a downstream side of the at least one swirl flow suppressor, an airflow, which flows from the radially outer side toward a radially central side around the axis in the through-passage, can be generated. This makes it possible to reduce the amount of the airflow, which flows from the through-passage toward the another side in the axial direction.

Therefore, it is possible to reduce the noise which is generated when the airflow passes through the through-passage. Accordingly, it is possible to provide the blower device configured to reduce the noise.

Furthermore, according to another aspect of the present disclosure, there is provided the blower device that includes:

• • an air conditioning case that has an inner wall, wherein the inner wall forms an air passage which is configured to conduct air;
  • a blower fan that is disposed in the air passage, wherein a direction, in which an axis of the blower fan extends, is defined as an axial direction, and the blower fan is configured to rotate toward one side in a rotational direction about the axis to draw in the air from one side in the axial direction and to blow the air out toward a radially outer side in a radial direction about the axis;
  • a cover that is disposed on another side in the axial direction with respect to the blower fan in the air passage and is formed to cover the blower fan from the another side in the axial direction, wherein the cover forms, between the cover and the inner wall, a through-passage that is configured to conduct the air blown out from the blower fan toward the another side in the axial direction; and
  • at least one swirl flow suppressor that is disposed in the through-passage and is elongated along the radial direction, wherein the at least one swirl flow suppressor is configured to suppress a swirl flow of the air generated by rotation of the blower fan, and thereby to generate an airflow that flows toward the another side in the axial direction, wherein:
  • an another-side end portion of the at least one swirl flow suppressor, which faces another side opposite to the one side in the rotational direction, is formed to extend toward the one side in the rotational direction as the another-side end portion extends from a radially inner side toward the radially outer side in the radial direction.

According to this aspect, when the swirl flow collides with the at least one swirl flow suppressor, the flow velocity of the air is reduced in comparison to a case where the at least one swirl flow suppressor is formed to extend from the radially inner side toward the radially outer side. This makes it possible to reduce noise generated when the swirl flow collides with the at least one swirl flow suppressor. Accordingly, it is possible to provide the blower device configured to reduce the noise.

Furthermore, according to another aspect of the present disclosure, there is provided a blower device that includes:

• • an air conditioning case that has an inner wall, wherein the inner wall forms an air passage which is configured to conduct air;
  • a blower fan that is disposed in the air passage, wherein a direction, in which an axis of the blower fan extends, is defined as an axial direction, and the blower fan is configured to rotate toward one side in a rotational direction about the axis to draw in the air from one side in the axial direction and to blow the air out toward a radially outer side in a radial direction about the axis;
  • a cover that is disposed on another side in the axial direction with respect to the blower fan in the air passage and is formed to cover the blower fan from the another side in the axial direction, wherein the cover forms, between the cover and the inner wall, a through-passage that is configured to conduct the air blown out from the blower fan toward the another side in the axial direction; and
  • at least one swirl flow suppressor that is disposed in the through-passage and is elongated along the radial direction, wherein the at least one swirl flow suppressor is configured to suppress a swirl flow of the air generated by rotation of the blower fan, and thereby to generate an airflow that flows toward the another side in the axial direction, wherein:
  • an another-side end portion of the at least one swirl flow suppressor, which faces another side opposite to the one side in the rotational direction, is formed to extend toward the another side in the rotational direction as the another-side end portion extends from a radially inner side toward the radially outer side in the radial direction.

According to this aspect, the at least one swirl flow suppressor can generate the airflow, in which the flow velocity of the air increases from the radially inner side toward the radially outer side in the radial direction. Furthermore, according to this aspect, it is possible to increase a difference between a flow velocity of the air on the radially inner side and a flow velocity of the air on the radially outer side in a flow velocity distribution of the airflow that has passed through the at least one swirl flow suppressor, as compared to a case where the at least one swirl flow suppressor is formed to extend from the radially inner side toward the radially outer side.

Accordingly, on the downstream side of the at least one swirl flow suppressor, the airflow, which flows from the radially outer side toward the radially central side around the axis in the through-passage, can be generated. This makes it possible to reduce the amount of the airflow, which flows from the through-passage toward the another side in the axial direction.

Therefore, it is possible to reduce the noise which is generated when the airflow passes through the through-passage. Accordingly, it is possible to provide the blower device configured to reduce the noise.

Additionally, according to another aspect of the present disclosure, there is provided a blower device that includes:

• • an air conditioning case that has an inner wall, wherein the inner wall forms an air passage which is configured to conduct air;
  • a blower fan that is disposed in the air passage, wherein a direction, in which an axis of the blower fan extends, is defined as an axial direction, and the blower fan is configured to rotate about the axis to draw in the air from one side in the axial direction and to blow the air out toward a radially outer side in a radial direction about the axis;
  • a cover that is disposed on another side in the axial direction with respect to the blower fan in the air passage and is formed to cover the blower fan from the another side in the axial direction, wherein the cover forms, between the cover and the inner wall, a through-passage that is configured to conduct the air blown out from the blower fan toward the another side in the axial direction; and
  • at least one swirl flow suppressor that is disposed in the through-passage and is elongated along the radial direction, wherein the at least one swirl flow suppressor is configured to suppress a swirl flow of the air generated by rotation of the blower fan, and thereby to generate an airflow that flows toward the another side in the axial direction, wherein:
  • a dimension of the at least one swirl flow suppressor, which is measured in a rotational direction of the blower fan, increases as the at least one swirl flow suppressor extends from a radially inner side toward the radially outer side in the radial direction.

Therefore, according to this aspect, the amount of the airflow, which passes through the radially outer side of the through-passage, is reduced in comparison to a case where the at least one swirl flow suppressor has a constant dimension measured in the rotational direction over the radial direction.

This makes it possible to reduce the noise which is generated when the airflow collides with the radially outer side of the at least one swirl flow suppressor. Therefore, it is possible to reduce the noise which is generated when the airflow passes through the through-passage. Accordingly, it is possible to provide the blower device configured to reduce the noise.

Additionally, according to another aspect of the present disclosure, there is provided a blower device that includes:

• • an air conditioning case that has an inner wall, wherein the inner wall forms an air passage which is configured to conduct air;
  • a blower fan that is disposed in the air passage, wherein a direction, in which an axis of the blower fan extends, is defined as an axial direction, and the blower fan is configured to rotate about the axis to draw in the air from one side in the axial direction and to blow the air out toward a radially outer side in a radial direction about the axis;
  • a cover that is disposed on another side in the axial direction with respect to the blower fan in the air passage and is formed to cover the blower fan from the another side in the axial direction, wherein the cover forms, between the cover and the inner wall, a through-passage that is configured to conduct the air blown out from the blower fan toward the another side in the axial direction; and
  • at least one swirl flow suppressor that is disposed in the through-passage and is elongated along the radial direction, wherein the at least one swirl flow suppressor is configured to suppress a swirl flow of the air generated by rotation of the blower fan, and thereby to generate an airflow that flows toward the another side in the axial direction, wherein:
  • a dimension of the at least one swirl flow suppressor, which is measured in a rotational direction of the blower fan, decreases as the at least one swirl flow suppressor extends from a radially inner side toward the radially outer side in the radial direction.

According to this aspect, the at least one swirl flow suppressor can generate the airflow, in which the flow velocity of the air increases from the radially inner side toward the radially outer side in the radial direction. Furthermore, according to this aspect, a pressure loss of the airflow, which passes through the through-passage, decreases from the radially inner side toward the radially outer side.

According to this, it is possible to increase a difference between the flow velocity of the air on the radially inner side and the flow velocity of the air on the radially outer side in the flow velocity distribution of the airflow that has passed through the at least one swirl flow suppressor, as compared to the case where the at least one swirl flow suppressor is formed to extend from the radially inner side toward the radially outer side.

Accordingly, on the downstream side of the at least one swirl flow suppressor, the airflow, which flows from the radially outer side toward the radially central side around the axis in the through-passage, can be generated. This makes it possible to reduce the amount of the airflow, which flows from the through-passage toward the another side in the axial direction.

Therefore, it is possible to reduce the noise which is generated when the airflow passes through the through-passage. Accordingly, it is possible to provide the blower device configured to reduce the noise.

Additionally, according to another aspect of the present disclosure, there is provided a blower device that includes:

• • an air conditioning case that has an inner wall, wherein the inner wall forms an air passage which is configured to conduct air;
  • a blower fan that is disposed in the air passage, wherein a direction, in which an axis of the blower fan extends, is defined as an axial direction, and the blower fan is configured to rotate toward one side in a rotational direction about the axis to draw in the air from one side in the axial direction and to blow the air out toward a radially outer side in a radial direction about the axis;
  • a cover that is disposed on another side in the axial direction with respect to the blower fan in the air passage and is formed to cover the blower fan from the another side in the axial direction, wherein the cover forms, between the cover and the inner wall, a through-passage that is configured to conduct the air blown out from the blower fan toward the another side in the axial direction; and
  • at least one swirl flow suppressor that is disposed in the through-passage and is elongated along the radial direction, wherein the at least one swirl flow suppressor is configured to suppress a swirl flow of the air generated by rotation of the blower fan, and thereby to generate an airflow that flows toward the another side in the axial direction, wherein:
  • an another-side end portion of the at least one swirl flow suppressor, which faces another side opposite to the one side in the rotational direction, is formed to extend toward the another side in the rotational direction as the another-side end portion extends from a radially inner side toward the radially outer side in the radial direction; and
  • a one-side end portion of the at least one swirl flow suppressor, which faces the one side in the axial direction, is formed to extend toward the one side in the axial direction as the one-side end portion extends from a radially inner side toward the radially outer side in the radial direction.

Therefore, according to this aspect, the at least one swirl flow suppressor is formed such that the at least one swirl flow suppressor extends toward the another side in the rotational direction as the at least one swirl flow suppressor extends from the radially inner side toward the radially outer side in the radial direction. Therefore, like in the aspects described above, the at least one swirl flow suppressor can reduce the noise which is generated when the airflow passes through the through-passage.

Furthermore, according to this aspect, the at least one swirl flow suppressor is formed such that the at least one swirl flow suppressor extends toward the one side in the axial direction as the at least one swirl flow suppressor extends from the radially inner side toward the radially outer side in the radial direction. Therefore, like in the aspects described above, it is possible to reduce the noise which is generated when the airflow passes through the through-passage. Accordingly, it is possible to provide the blower device configured to reduce the noise.

Additionally, according to another aspect of the present disclosure, there is provided a blower device that includes:

• • an air conditioning case that has an inner wall, wherein the inner wall forms an air passage which is configured to conduct air;
  • a blower fan that is disposed in the air passage, wherein a direction, in which an axis of the blower fan extends, is defined as an axial direction, and the blower fan is configured to rotate toward one side in a rotational direction about the axis to draw in the air from one side in the axial direction and to blow the air out toward a radially outer side in a radial direction about the axis;
  • a cover that is disposed on another side in the axial direction with respect to the blower fan in the air passage and is formed to cover the blower fan from the another side in the axial direction, wherein the cover forms, between the cover and the inner wall, a through-passage that is configured to conduct the air blown out from the blower fan toward the another side in the axial direction; and
  • at least one swirl flow suppressor that is disposed in the through-passage and is elongated along the radial direction, wherein the at least one swirl flow suppressor is configured to suppress a swirl flow of the air generated by rotation of the blower fan, and thereby to generate an airflow that flows toward the another side in the axial direction, wherein:
  • an another-side end portion of the at least one swirl flow suppressor, which faces another side opposite to the one side in the rotational direction, is formed to extend toward the one side in the rotational direction as the another-side end portion extends from a radially inner side toward the radially outer side in the radial direction; and
  • a one-side end portion of the at least one swirl flow suppressor, which faces the one side in the axial direction, is formed to extend toward the one side in the axial direction as the one-side end portion extends from a radially inner side toward the radially outer side in the radial direction.

Therefore, according to this aspect, the at least one swirl flow suppressor is formed such that the at least one swirl flow suppressor extends toward the one side in the rotational direction as the at least one swirl flow suppressor extends from the radially inner side toward the radially outer side in the radial direction. Therefore, like in the aspects described above, it possible to reduce the noise which is generated when the swirl flow blown from the blower fan collides with the at least one swirl flow suppressor.

Furthermore, according to this aspect, the at least one swirl flow suppressor is formed such that the at least one swirl flow suppressor extends toward the one side in the axial direction as the at least one swirl flow suppressor extends from the radially inner side toward the radially outer side in the radial direction. Therefore, like in the aspects described above, it is possible to reduce the noise which is generated when the airflow passes through the through-passage.

Accordingly, it is possible to provide the blower device configured to reduce the noise.

Additionally, according to another aspect of the present disclosure, there is provided a blower device that includes:

• • an air conditioning case that has an inner wall, wherein the inner wall forms an air passage which is configured to conduct air;
  • a blower fan that is disposed in the air passage, wherein a direction, in which an axis of the blower fan extends, is defined as an axial direction, and the blower fan is configured to rotate toward one side in a rotational direction about the axis to draw in the air from one side in the axial direction and to blow the air out toward a radially outer side in a radial direction about the axis;
  • a cover that is disposed on another side in the axial direction with respect to the blower fan in the air passage and is formed to cover the blower fan from the another side in the axial direction, wherein the cover forms, between the cover and the inner wall, a through-passage that is configured to conduct the air blown out from the blower fan toward the another side in the axial direction; and
  • at least one swirl flow suppressor that is disposed in the through-passage and is elongated along the radial direction, wherein the at least one swirl flow suppressor is configured to suppress a swirl flow of the air generated by rotation of the blower fan, and thereby to generate an airflow that flows toward the another side in the axial direction, wherein:
  • an another-side end portion of the at least one swirl flow suppressor, which faces another side opposite to the one side in the rotational direction, is formed to extend toward the another side in the rotational direction as the another-side end portion extends from a radially inner side toward the radially outer side in the radial direction; and
  • a one-side end portion of the at least one swirl flow suppressor, which faces the one side in the axial direction, is formed to extend toward the another side in the axial direction as the one-side end portion extends from a radially inner side toward the radially outer side in the radial direction.

Therefore, according to this aspect, the at least one swirl flow suppressor is formed such that the at least one swirl flow suppressor extends toward the another side in the rotational direction as the at least one swirl flow suppressor extends from the radially inner side toward the radially outer side in the radial direction. Therefore, like in the aspects described above, it is possible to reduce the noise which is generated when the airflow passes through the through-passage.

Furthermore, according to this aspect, the at least one swirl flow suppressor is formed such that the at least one swirl flow suppressor extends toward the another side in the axial direction as the at least one swirl flow suppressor extends from the radially inner side toward the radially outer side in the radial direction. Therefore, like in the aspects described above, it possible to reduce the noise which is generated when the swirl flow blown from the blower fan collides with the at least one swirl flow suppressor. Accordingly, it is possible to provide the blower device configured to reduce the noise.

Additionally, according to another aspect of the present disclosure, there is provided a blower device that includes:

• • an air conditioning case that has an inner wall, wherein the inner wall forms an air passage which is configured to conduct air;
  • a blower fan that is disposed in the air passage, wherein a direction, in which an axis of the blower fan extends, is defined as an axial direction, and the blower fan is configured to rotate toward one side in a rotational direction about the axis to draw in the air from one side in the axial direction and to blow the air out toward a radially outer side in a radial direction about the axis;
  • a cover that is disposed on another side in the axial direction with respect to the blower fan in the air passage and is formed to cover the blower fan from the another side in the axial direction, wherein the cover forms, between the cover and the inner wall, a through-passage that is configured to conduct the air blown out from the blower fan toward the another side in the axial direction; and
  • at least one swirl flow suppressor that is disposed in the through-passage and is elongated along the radial direction, wherein the at least one swirl flow suppressor is configured to suppress a swirl flow of the air generated by rotation of the blower fan, and thereby to generate an airflow that flows toward the another side in the axial direction, wherein:
  • an another-side end portion of the at least one swirl flow suppressor, which faces another side opposite to the one side in the rotational direction, is formed to extend toward the one side in the rotational direction as the another-side end portion extends from a radially inner side toward the radially outer side in the radial direction; and
  • a one-side end portion of the at least one swirl flow suppressor, which faces the one side in the axial direction, is formed to extend toward the another side in the axial direction as the one-side end portion extends from a radially inner side toward the radially outer side in the radial direction.

Therefore, according to this aspect, the at least one swirl flow suppressor is formed such that the at least one swirl flow suppressor extends toward the one side in the rotational direction as the at least one swirl flow suppressor extends from the radially inner side toward the radially outer side in the radial direction. Therefore, like in the aspect described above, it possible to reduce the noise which is generated when the swirl flow blown from the blower fan collides with the at least one swirl flow suppressor.

Furthermore, according to this aspect, the at least one swirl flow suppressor is formed such that the at least one swirl flow suppressor extends toward the another side in the axial direction as the at least one swirl flow suppressor extends from the radially inner side toward the radially outer side in the radial direction.

Therefore, like in the aspects described above, it possible to reduce the noise which is generated when the swirl flow blown from the blower fan collides with the at least one swirl flow suppressor. Accordingly, it is possible to provide the blower device configured to reduce the noise.

Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. For the sake of simplicity of explanation, the same reference signs are assigned to the portions that are the same or equal to each other in the following respective embodiments.

First Embodiment

As shown in FIG. 1, a vehicle air-conditioning unit 10 of the present embodiment includes an air-conditioning case 12, an evaporator 16, a heater core 18, an electric blower 20, a plurality of doors 21, 22, 23, 24a, 24b, 25 and a flow straightener mechanism 26.

The vehicle air-conditioning unit 10 is, for example, disposed inside an instrument panel provided at a foremost portion of a vehicle cabin. Arrows DR1, DR2 in FIG. 1 indicate an orientation of a vehicle in which the vehicle air-conditioning unit 10 is mounted.

That is, the arrow DR1 in FIG. 1 indicates a vehicle front-rear direction DR1, and the arrow DR2 indicates a vehicle up-down direction DR2. These directions DR1, DR2 are intersecting directions, and more precisely, directions orthogonal to each other.

The air-conditioning case 12 is a member that is made of resin and forms an outer shell of the vehicle air-conditioning unit 10. The air-conditioning case 12 has an outside air inlet 121, an inside air inlet 122, and discharge ports 126, 127, 128 for discharging air from inside the air-conditioning case 12.

A case internal air passage 123 is formed inside the air-conditioning case 12, and the case internal air passage 123 conducts the air from one or both of the outside air inlet 121 and the inside air inlet 122 toward each of the discharge ports 126, 127, 128. The case internal air passage 123 is formed to extend in the vehicle front-rear direction DR1.

The outside air inlet 121 is an inlet for introducing outside air, which is air outside the vehicle cabin, into the case internal air passage 123. The inside air inlet 122 is an inlet for introducing inside air, which is air inside the vehicle cabin, into the case internal air passage 123. The outside air and/or inside air are introduced into the air-conditioning case 12 by the electric blower 20.

The outside air inlet 121 and the inside air inlet 122 are opened and closed by an inside-outside air switching door 25. Then, the air introduced from one or both of the outside air inlet 121 and the inside air inlet 122 flows into the evaporator 16.

The evaporator 16 is a cooling heat exchanger that cools the air passing through the evaporator 16. In short, the evaporator 16 is a cooling device.

The evaporator 16 is received in the air-conditioning case 12. That is, the evaporator 16 is disposed in the case internal air passage 123 and is arranged so that the outside air or the inside air, which is introduced into the case internal air passage 123, flows into the evaporator 16.

The evaporator 16, together with a compressor, a condenser and an expansion valve (not shown), constitutes a known refrigeration cycle apparatus that circulates a refrigerant. The evaporator 16 causes heat exchange between the air passing through the evaporator 16 and the refrigerant, thereby evaporating the refrigerant and cooling the air.

The electric blower 20 includes: a blower fan 201, which is disposed in the case internal air passage 123 and rotates about a fan axis CL1; and an electric motor (not shown) that rotationally drives the blower fan 201. The blower fan 201 is a centrifugal fan in the present embodiment.

That is, the electric blower 20 is a centrifugal blower that draws in the air from one side in a fan axial direction DRa of the fan axis CL1 by rotation of the blower fan 201 and blows out the drawn-in air toward a radially outer side in a radial direction Kc1 of the blower fan 201.

Here, the air, which is blown toward the radially outer side in the radial direction Kc1 by the electric blower 20, is guided by the air-conditioning case 12 toward a downstream side of the case internal air passage 123 in a flow direction of the air, as indicated by an arrow FLf (for example, toward the rear side of the vehicle in FIG. 1). The fan axial direction DRa is a direction in which the fan axis CL1 extends.

More specifically, the electric blower 20 has a fan air inlet 201a and a fan air outlet 201b. The fan air inlet 201a is an inlet, which is provided on the one side in the fan axial direction DRa of the fan axis CL1 with respect to the blower fan 201 to draw in the air. The fan air outlet 201b is an outlet, which is formed over the entire circumference of an outer peripheral portion centered on the fan axis CL1 with respect to the blower fan 201 to blow out the air.

The blower fan 201 draws in the air from the one side in the fan axial direction DRa through the fan air inlet 201a when the blower fan 201 is rotated about the fan axis CL1. Along with this, the blower fan 201 blows the drawn-in air out from the fan air outlet 201b toward the radially outer side in the radial direction Kc1 of the blower fan 201 about the fan axis CL1.

In the case internal air passage 123 of the air-conditioning case 12, a fan surrounding space 123b, into which the air blown from the blower fan 201 flows, is formed on a radially outer side of the blower fan 201 in the radial direction Kc1 about the fan axis CL1.

The fan surrounding space 123b is provided between an inner wall 12a of the air-conditioning case 12, which forms the case internal air passage 123, and the blower fan 201.

The air-conditioning case 12 of the present embodiment is configured to guide the air, which is blown from the blower fan 201 into the fan surrounding space 123b, toward the other side, which is opposite to the one side, in the fan axial direction DRa.

For example, an unillustrated airflow guide wall is provided in the air-conditioning case 12 on the one side of the fan surrounding space 123b in the fan axial direction DRa. In the air-conditioning case 12, the airflow guide wall guides the air in the fan surrounding space 123b such that the air flows toward the other side in the fan axial direction DRa, while preventing the air from flowing toward the one side in the fan axial direction DRa.

As a result, the air, which is blown from the blower fan 201 toward the radially outer side in the radial direction Kc1, enters the fan surrounding space 123b, as indicated by the arrow FLf. Then, the air is guided by the air-conditioning case 12 from the fan surrounding space 123b toward the other side of the blower fan 201 in the fan axial direction DRa.

The fan axial direction DRa of the fan axis CL1 coincides with the vehicle front-rear direction DR1 in the present embodiment. The fan axial direction DRa of the fan axis CL1 is also referred to simply as the fan axial direction DRa. The radial direction Kc1 of the blower fan 201 is a radial direction Kc1 about the fan axis CL1.

The electric blower 20 has a so-called suction layout in which the blower fan 201 is disposed on the downstream side of the evaporator 16 in the airflow direction. The electric blower 20 is arranged such that a side of the electric blower 20, which faces the one side in the fan axial direction DRa and is an air intake side of the blower fan 201, faces an air outlet surface 16b of the evaporator 16.

Accordingly, the blower fan 201 is disposed such that an opposite side of the blower fan 201, which faces the other side in the fan axial direction DRa of the fan axis CL1 and is opposite to the one side in the fan axial direction DRa, faces toward the downstream side in the airflow direction in the case internal air passage 123.

The heater core 18 is disposed on the downstream side of the blower fan 201 in the airflow direction in the case internal air passage 123. The heater core 18 is disposed at a center portion which is centered in the vehicle up-down direction DR2 within the case internal air passage 123. The heater core 18 is a heating device that heats the air, which passes through the heater core 18 among the air flowing through the case internal air passage 123.

In the air-conditioning case 12, an upper bypass passage 125a is formed on the upper side of the heater core 18, and a lower bypass passage 125b is formed on a lower side of the heater core 18. The upper bypass passage 125a and the lower bypass passage 125b are each included in the case internal air passage 123 and allow the air to flow in parallel with respect to the heater core 18.

That is, both the upper bypass passage 125a and the lower bypass passage 125b are bypass passages that allow the air to flow while bypassing the heater core 18.

An air mix door 24a and an air mix door 24b are located on the upstream side of the heater core 18 in the airflow direction in the case internal air passage 123. The air mix doors 24a, 24b are provided on the downstream side of the flow straightener mechanism 26 in the airflow direction.

In other words, the air mix doors 24a, 24b are provided on the other side of the flow straightener mechanism 26 in the fan axial direction DRa. The heater core 18 and the bypass passages 125a, 125b are provided on the other side of the air mix doors 24a, 24b in the fan axial direction DRa.

The air mix door 24a is disposed in the upper bypass passage 125a and opens and closes the upper bypass passage 125a. The air mix door 24a is a sliding door mechanism and is slid by an electric actuator (not shown).

The air mix door 24a adjusts an airflow amount ratio between the amount of the airflow, which passes through the heater core 18, and the amount of the airflow, which passes through the upper bypass passage 125a, in accordance with a sliding position of the air mix door 24a.

The air mix door 24b is disposed in the lower bypass passage 125b and opens and closes the lower bypass passage 125b. The air mix door 24b is a sliding door mechanism and is slid by an electric actuator (not shown).

The air mix door 24b adjusts an airflow amount ratio between the amount of the airflow, which passes through the heater core 18, and the amount of the airflow, which passes through the lower bypass passage 125b, in accordance with a sliding position of the air mix door 24b.

The air-conditioning case 12 has a face discharge port 126, a defroster discharge port 127 and a foot discharge port 128 for discharging the air to the outside of the air-conditioning case 12.

The face discharge port 126, the defroster discharge port 127 and the foot discharge port 128 are respectively connected to the case internal air passage 123 on the downstream side of the heater core 18 and the bypass passage 125a, 125b in the airflow direction.

The air, which is discharged from the face discharge port 126, is guided through a duct (not shown) and is blown toward a face or chest of an occupant seated in a front seat in the vehicle cabin. The air, which is discharged from the defroster discharge port 127, is guided through a duct (not shown) and is blown toward a front window glass of the vehicle in the vehicle cabin. The air, which is discharged from the foot discharge port 128, is guided through a duct (not shown) and is blown toward feet of the occupant seated in the front seat in the vehicle cabin.

A face door 21 is provided at the face discharge port 126, and the face door 21 opens and closes the face discharge port 126. A defroster door 22 is provided at the defroster discharge port 127, and the defroster door 22 opens and closes the defroster discharge port 127. Afoot door 23 is provided at the foot discharge port 128, and the foot door 23 opens and closes the foot discharge port 128.

The warm air, which has passed through the heater core 18, and the cool air, which have passed through the upper bypass passage 125a, are mixed on the downstream side of the heater core 18 in the airflow direction in the case internal air passage 123. Then, the mixed air is mainly blown into the vehicle cabin from whichever is open among the face discharge port 126 and the defroster discharge port 127.

Also, the warm air, which is blown from the heater core 18, and the cool air, which have passed through the lower bypass passage 125b, are mixed on the downstream side of the heater core 18 in the airflow direction. Furthermore, when the foot discharge port 128 is open, the mixed air is mainly blown into the vehicle cabin from the foot discharge port 128.

As shown in FIG. 1, in the airflow direction in the case internal air passage 123, the flow straightener mechanism 26 is disposed on the downstream side of the blower fan 201 and on the upstream side of the heater core 18 and the air mix doors 24a, 24b.

Accordingly, the air, which is blown from the blower fan 201, flows into the flow straightener mechanism 26, and the blown airflows to the bypass passages 125a, 125b or the heater core 18 after passing through the flow straightener mechanism 26.

Here, the blower fan 201 is disposed such that the side of the blower fan 201, which faces the other side in the fan axial direction DRa, faces the downstream side of the airflow in the case internal air passage 123.

The flow straightener mechanism 26 of the present embodiment suppresses a swirl flow generated by the rotation of the blower fan 201 and thereby generates an airflow that flows toward the other side in the fan axial direction DRa. The swirl flow is an airflow that swirls about the fan axis CL1. Specifically, as shown in FIG. 2, the flow straightener mechanism 26 includes a cover 26a and a plurality of swirl flow suppressors 26b.

The cover 26a is shaped in a circular plate form that covers the blower fan 201 from the other side in the fan axial direction DRa. A through-passage 130 is formed between the cover 26a and the inner wall 12a of the air-conditioning case 12. The through-passage 130 constitutes a part of the case internal air passage 123.

As shown in FIG. 2, the swirl flow suppressors 26b are each disposed between the cover 26a and the inner wall 12a. The swirl flow suppressors 26b are arranged at intervals in a circumferential direction about the fan axis CL1.

A radially outer end part of each of the swirl flow suppressors 26b, which faces an outer side in the radial direction Kc1, is joined to the inner wall 12a. A radially inner end part of each of the swirl flow suppressors 26b, which faces an inner side in the radial direction Kc1, is joined to the cover 26a. The swirl flow suppressors 26b divide the through-passage 130 into a plurality of sub-passages 130a.

In the flow straightener mechanism 26 of the present embodiment, the number of the swirl flow suppressors 26b is eight, and thereby the number of the sub-passages 130a formed by the swirl flow suppressors 26b is eight.

The sub-passages 130a are formed such that a circumferential distance increases from the radially inner side toward the radially outer side in the radial direction Kc1. The swirl flow suppressors 26b suppress the swirl flow flowing through the sub-passages 130a and generate an airflow flowing toward the other side in the fan axial direction DRa.

Hereinafter, for convenience of explanation, an interval between corresponding adjacent two of the swirl flow suppressors 26b is referred to as interval Kn, as shown in FIG. 2. The swirl flow suppressors 26b of the present embodiment are arranged in the circumferential direction such that two or more of the intervals Kn are different from each other. For example, the flow straightener mechanism 26 is configured such that the intervals Kn of the eight sub-passages 130a are different from one another.

As a result, the frequencies of noise, which is generated when the swirl flow is guided by the swirl flow suppressors 26b, are dispersed. As shown in FIG. 3, the swirl flow suppressors 26b are each formed in a backwardly inclined shape such that the swirl flow suppressor 26b extends toward the other side in the fan axial direction DRa as the swirl flow suppressor 26b extends from the radially inner side toward the radially outer side in the radial direction Kc1.

In each of the swirl flow suppressors 26b, an end surface 270 (serving as a one-side end portion) is formed on the one side of the swirl flow suppressor 26b in the fan axial direction DRa and is elongated along the radial direction Kc1. The end surface 270 of each of the swirl flow suppressors 26b is formed such that the end surface 270 extends toward the other side in the fan axial direction DRa as the end surface 270 extends from the radially inner side toward the radially outer side in the radial direction Kc1.

An end part of each end surface 270, which is located radially outermost in the radial direction Kc1 in the end surface 270, is defined as a radially outer end part 271. An end part of each end surface 270, which is located radially innermost in the radial direction Kc1 in the end surface 270, is defined as a radially inner end part 272.

Here, a distance between the radially outer end part 271 and the radially inner end part 272 measured in the fan axial direction DRa is defined as an axial distance dDR.

The swirl flow suppressors 26b of the present embodiment include at least two swirl flow suppressors 26b, the axial distances dDR of which are different from each other. For example, the swirl flow suppressors 26b are configured such that the axial distances dDR of all of the swirl flow suppressors 26b are different from each other.

As a result, the frequencies of noise, which is generated when the swirl flow is guided by the swirl flow suppressors 26b, are dispersed.

As shown in FIG. 4, the flow straightener mechanism 26 is configured such that, when light is projected from a light source 300 onto the flow straightener mechanism 26 from the one side in the fan axial direction DRa, shadows cast by the swirl flow suppressors 26b onto a wall 301 are offset from one another.

That is, the flow straightener mechanism 26 is formed so as to avoid overlap of the shadows, which are cast by the swirl flow suppressors 26b, when the flow straightener mechanism 26 is optically projected with the light from the light source 300 on the one side of the swirl flow suppressor 26b in the fan axial direction DRa.

This configuration allows the flow straightener mechanism 26, which is a molded product made of a resin material or a metal material, to be easily removed from a mold by moving the mold toward either the one side or the other side in the fan axial direction DRa during injection molding.

FIG. 4 illustrates an example in which the light source 300 is disposed on the one side of the flow straightener mechanism 26 in the fan axial direction DRa, and the wall 301 is disposed on the other side of the flow straightener mechanism 26 in the fan axial direction DRa.

In the present embodiment, the flow straightener mechanism 26, the blower fan 201 and the air-conditioning case 12 form the blower device 100.

Next, the operation of the vehicle air-conditioning unit 10 will be described.

First, when the operation of the electric blower 20 starts, as shown in FIG. 1, the air is introduced into the case internal air passage 123, which is formed in the air-conditioning case 12, through either the outside air inlet 121 or the inside air inlet 122. The air, which is introduced into the case internal air passage 123, is cooled by the evaporator 16 while passing through the evaporator 16.

The air, which is cooled by the evaporator 16, is drawn into the blower fan 201 of the electric blower 20, blown out toward the radially outer side of the blower fan 201 in the radial direction Kc1, and introduced into the fan surrounding space 123b.

Accordingly, the air, which is introduced into the fan surrounding space 123b, is guided to the flow straightener mechanism 26 by the air-conditioning case 12.

The air, which is guided from the fan surrounding space 123b to the flow straightener mechanism 26, includes the swirl flow generated by the rotation of the blower fan 201. In the swirl flow, the flow velocity of the air increases from the radially inner side toward the radially outer side in the radial direction Kc1 about the fan axis CL1.

The swirl flow from the fan surrounding space 123b collides with each of the swirl flow suppressors 26b of the flow straightener mechanism 26. At this time, each of the swirl flow suppressors 26b suppresses the swirl flow and thereby generates the airflow that flows toward the other side in the fan axial direction DRa.

Here, as described above, the swirl flow suppressors 26b are each formed in the backwardly inclined shape such that the end surface 270 of each swirl flow suppressor 26b extends toward the other side in the fan axial direction DRa as the swirl flow suppressor 26b extends from the radially inner side toward the radially outer side in the radial direction Kc1.

Accordingly, in the present embodiment, compared to a comparative example in which a plurality of swirl flow suppressors 26b are formed to extend linearly in the radial direction Kc1, it is possible to reduce the flow velocity of the swirl flow that collides with the swirl flow suppressors 26b.

Thus, compared to the swirl flow suppressors 26b of the above-described comparative example, it is possible to reduce noise that is generated when the swirl flow collides with the plurality of swirl flow suppressors 26b.

In addition, in the case of the comparative example in which the swirl flow suppressors 26b are arranged at equal intervals in the circumferential direction, the frequency of noise that is generated when the swirl flow collides with the plurality of swirl flow suppressors 26b is confined to a narrow frequency range.

In contrast, the swirl flow suppressors 26b of the present embodiment are arranged in the circumferential direction such that the intervals Kn of these swirl flow suppressors 26b are different from each other. Accordingly, compared to the comparative example in which the swirl flow suppressors 26b are arranged at the equal intervals in the circumferential direction, the present embodiment can broaden the frequency range of the noise that is generated when the swirl flow collides with the swirl flow suppressors 26b.

In addition, the swirl flow suppressors 26b of the present embodiment are configured such that the axial distances dDR of all of the swirl flow suppressors 26b are different from each other. Therefore, compared with the comparative example in which the swirl flow suppressors 26b are formed to extend linearly in the radial direction Kc1, the frequency range of the noise generated when the swirl flow collides with the swirl flow suppressors 26b can be broadened.

In this manner, the swirl flow is guided by the swirl flow suppressors 26b and flows toward the other side in the fan axial direction DRa. The air, which flows toward the other side in the fan axial direction DRa, becomes the warm air after passing through the heater core 18 and flows to the downstream side of the heater core 18 in the airflow direction. In contrast, the air, which flows toward the other side in the fan axial direction DRa, remains the cool air after passing through the bypass passages 125a, 125b and flows to the downstream side of the heater core 18 in the airflow direction.

Then, the warm air and the cool air are mixed together at the downstream side of the heater core 18 in the airflow direction, and the mixed air is blown into a predetermined area in the vehicle cabin from whichever of the face discharge port 126, the defroster discharge port 127 and the foot discharge port 128 is open.

According to the present embodiment described above, the vehicle air-conditioning unit 10 includes the air-conditioning case 12 that has the inner wall 12a, which forms the case internal air passage 123 configured to conduct the air.

The vehicle air-conditioning unit 10 includes the blower fan 201 that is disposed in the case internal air passage 123 and is configured to rotate about the fan axis CL1 to draw in the air from the one side in the fan axial direction DRa and blow the air out toward the radially outer side in the radial direction Kc1 about the fan axis CL1.

The vehicle air-conditioning unit 10 includes the cover 26a that is disposed on the other side in the fan axial direction DRa with respect to the blower fan 201 in the case internal air passage 123 and is formed to cover the blower fan 201 from the other side in the fan axial direction DRa.

The cover 26a forms, between the cover 26a and the inner wall 12a of the air-conditioning case 12, the through-passage 130 that is configured to conduct the air blown out from the blower fan 201 toward the other side in the fan axial direction DRa.

The vehicle air-conditioning unit 10 includes the swirl flow suppressors 26b that are disposed in the through-passage 130 and are each elongated along the radial direction Kc1 about the fan axis CL1. Each of the swirl flow suppressors 26b is configured to suppress the swirl flow of the air generated by the rotation of the blower fan 201, and thereby to generate the airflow that flows toward the other side in the fan axial direction DRa.

The end surface 270 of each of the swirl flow suppressors 26b is formed to extend toward the other side in the fan axial direction DRa as the end surface 270 extends from the radially inner side toward the radially outer side in the radial direction Kc1 about the fan axis CL1.

Therefore, according to the present embodiment, compared with the case where the swirl flow suppressors 26b are formed to extend linearly from the radially inner side toward the radially outer side in the radial direction Kc1, the flow velocity of the swirl flow, which collides with the swirl flow suppressors 26b, can be reduced.

As a result, the noise, which is generated when the air blown from the blower fan 201 collides with the swirl flow suppressors 26b, can be reduced. Accordingly, it is possible to provide the blower device 100 configured to reduce the noise.

In the vehicle air-conditioning unit 10 according to the present embodiment configured as described above, the following advantages (a), (b) and (c) are obtained.

(a) The swirl flow suppressors 26b of the present embodiment are arranged in the circumferential direction about the fan axis CL1 such that the intervals Kn pf all of the swirl flow suppressors 26b are different from each other. Therefore, the frequencies of the noise, which is generated when the swirl flow is guided by the swirl flow suppressors 26b, can be dispersed. Accordingly, discomfort caused by the noise to the user can be reduced.

(b) The swirl flow suppressors 26b are configured such that the axial distances dDR of all of the swirl flow suppressors 26b are different from each other. The axial distance dDR is the distance between the radially outer end part 271 and the radially inner end part 272 measured in the fan axial direction DRa.

Therefore, the frequencies of the noise, which is generated when the air collides with the swirl flow suppressors 26b, can be dispersed. Accordingly, the discomfort caused by the noise to the user can be reduced.

(c) The swirl flow suppressors 26b are arranged so as to avoid overlap of the respective shadows of the swirl flow suppressors 26b that are generated when the swirl flow suppressors 26b are optically projected from the one side in the fan axial direction DRa.

As a result, when the flow straightener mechanism 26 is injection-molded, it becomes possible to easily release the molded flow straightener mechanism (a molded article) 26 from the mold by moving the mold toward the one side or the other side in the fan axial direction DRa.

Second Embodiment

In a flow straightener mechanism 26 of the second embodiment, an example will be described with reference to FIG. 5, in which each of the swirl flow suppressors 26b of the flow straightener mechanism 26 of the first embodiment is formed in a curved shape that is convex toward the one side in the fan axial direction DRa.

FIG. 5 is a cross-sectional view of the blower fan and the flow straightener mechanism according to the present embodiment, taken along a virtual plane including the fan axis.

According to the present embodiment described above, each of the swirl flow suppressors 26b is formed in the curved shape that is convex toward the one side in the fan axial direction DRa. Accordingly, it is possible to provide the blower device 100 configured to further reduce the noise.

Third Embodiment

In the third embodiment, with reference to FIGS. 6 to 10, there will be described an example, in which an inclination angle of each of the end surfaces (axial end surfaces) 27a, 27b of each swirl flow suppressor 26b of the first embodiment decreases from the radially inner side toward the radially outer side in the radial direction Kc1.

The present embodiment differs from the above-described first embodiment only in the configuration of the swirl flow suppressors 26b. Accordingly, the following description mainly focuses on the configuration of the swirl flow suppressors 26b.

FIG. 6 is a cross-sectional view of the flow straightener mechanism 26 of the present embodiment taken along a virtual plane perpendicular to the fan axis CL1. FIG. 7 is a cross-sectional view taken along line VII-VII in FIG. 6. FIG. 8 is a cross-sectional view taken along line VIII-VIII in FIG. 6, and FIG. 9 is a cross-sectional view taken along line IX-IX in FIG. 6. FIGS. 7, 8 and 9 are the cross-sectional views of one swirl flow suppressor 26b among the plurality of swirl flow suppressors 26b.

FIG. 7 is a cross-sectional view of a section of the swirl flow suppressor 26b, which is located on the radially outer side of the cross-section shown in FIG. 8 in the radial direction Kc1. FIG. 8 is a cross-sectional view of a section of the swirl flow suppressor 26b, which is located on the radially outer side of the cross-section shown in FIG. 9 in the radial direction Kc1.

Each of the swirl flow suppressors 26b includes a front-side guide 280 and a rear-side guide 281, as shown in FIGS. 7, 8 and 9.

The front-side guide 280 is elongated along the rotational direction Ka1 of the blower fan 201. The rear-side guide 281 is formed to extend from a one end part of the front-side guide 280, which faces the one side in the rotational direction Ka1, toward the other side in the fan axial direction DRa.

The front-side guide 280 of the present embodiment is formed to extend toward the other side in the fan axial direction DRa as the front-side guide 280 extends from the radially inner side toward the radially outer side in the radial direction Kc1. Thereby, each of the swirl flow suppressors 26b is formed in a backwardly inclined shape such that the swirl flow suppressor 26b extends toward the other side in the fan axial direction DRa as the swirl flow suppressor 26b extends from the radially inner side toward the radially outer side in the radial direction Kc1 about the fan axis CL1.

The front-side guide 280 is formed such that an axis AZ1 of the front-side guide 280 intersects with a reference line KJ1. The axis AZ1 is a virtual line that indicates an axis of the front-side guide 280. The reference line KJ1 is a virtual line that is perpendicular to both the fan axial direction DRa and the radial direction Kc1 and is parallel to the rotational direction Ka1.

As shown in FIGS. 7, 8 and 9, the front-side guide 280 is formed such that an acute angle θ1, which is defined between the axis AZ1 and the reference line KJ1, decreases as the front-side guide 280 extends from the radially inner side toward the radially outer side in the radial direction Kc1. The acute angle refers to an angle that is larger than 0 degrees and is smaller than 180 degrees.

Each of the swirl flow suppressors 26b has two end surface 27a, 28a, which face the one side in the fan axial direction DRa. Also, each of the swirl flow suppressors 26b has two end surface 27b, 28b, which face the other side in the fan axial direction DRa.

The end surface 27a is disposed on the one side of the end surface 28a in the rotational direction Ka1. The end surface 27a is formed to extend from a one-side end of the end surface 28a, which faces the one side in the rotational direction Ka1, toward the one side in the rotational direction Ka1.

The end surface 27b is disposed on the one side of the end surface 28b in the rotational direction Ka1. The end surface 27b is formed to extend from a one-side end of the end surface 28b, which faces the one side in the rotational direction Ka1, toward the one side in the rotational direction Ka1. The end surface 27a of each of the swirl flow suppressors 26b is formed to extend toward the other side in the fan axial direction DRa as the end surface 27a extends from the radially inner side toward the radially outer side in the radial direction Kc1 about the fan axis CL1.

FIGS. 10, 11 and 12 respectively show an acute angle θ2, which is defined between a virtual plane Sa and the end surface 27a, and an acute angle θ3, which is defined between the virtual plane Sa and the end surface 27b. FIG. 10 shows the acute angle θ2, which is defined between the end surface 27a and the virtual plane Sa in FIG. 7, and the acute angle θ3, which is defined between the end surface 27b and the virtual plane Sa in FIG. 7. The virtual plane Sa is a plane that is parallel to the rotational direction Ka1 and is perpendicular to the fan axial direction DRa.

FIG. 11 shows the acute angle θ2, which is defined between the end surface 27a and the virtual plane Sa in FIG. 8, and the acute angle θ3, which is defined between the end surface 27b and the virtual plane Sa in FIG. 8. FIG. 12 shows the acute angle θ2, which is defined between the end surface 27a and the virtual plane Sa in FIG. 9, and the acute angle θ3, which is defined between the end surface 27b and the virtual plane Sa in FIG. 9.

In the front-side guide 280 of each of the swirl flow suppressors 26b of the present embodiment, each of the end surfaces 27a, 27b is inclined such that the acute angle θ2, θ3 (i.e., the inclination angle) decreases as the end surface 27a, 27b extends from the radially inner side toward the radially outer side in the radial direction Kc1.

According to the present embodiment described above, each of the swirl flow suppressors 26b is formed in the backwardly inclined shape such that the swirl flow suppressor 26b extends toward the other side in the fan axial direction DRa as the swirl flow suppressor 26b extends from the radially inner side toward the radially outer side in the radial direction Kc1 about the fan axis CL1.

Therefore, like in the first embodiment, the noise, which is generated when the air blown from the blower fan 201 collides with the swirl flow suppressors 26b, can be reduced. Accordingly, it is possible to provide the blower device 100 configured to reduce the noise.

In the present embodiment, in each of the swirl flow suppressors 26b, each acute angle θ2, θ3, which is defined between the virtual plane Sa and the corresponding one of the end surfaces 27a, 27b, decreases from the radially inner side toward the radially outer side in the radial direction Kc1. Accordingly, the pressure loss of the swirl flow, which is caused by the end surfaces 27a, 27b, decreases from the radially inner side toward the radially outer side in the radial direction Kc1.

Here, the swirl flow has a higher flow velocity on the radially outer side in the radial direction Kc1 than on the radially inner side in the radial direction Kc1. Accordingly, by reducing the pressure loss caused by the swirl flow, which flows on the radially outer side in the radial direction Kc1, the overall pressure loss can be efficiently reduced.

Fourth Embodiment

In the first embodiment described above, the example is described in which the dimension of each of the swirl flow suppressors 26b, which is measured in the rotational direction Ka1, is uniform over the entire extent of the swirl flow suppressor 26b in the radial direction Kc1.

In place of this, in the fourth embodiment, an example will be described with reference to FIGS. 13, 14, 15 and 16, in which a dimension dDa of each of the swirl flow suppressors 26b measured in the rotational direction Ka1 increases as the swirl flow suppressor 26b extends from the radially inner side toward the radially outer side in the radial direction Kc1.

FIG. 13 is a cross-sectional view of the flow straightener mechanism 26 of the present embodiment, taken along a virtual plane perpendicular to the fan axis CL1, and FIG. 14 is a cross-sectional view taken along line XIV-XIV in FIG. 13. FIG. 15 is a cross-sectional view taken along line XV-XV in FIG. 13, and FIG. 16 is a cross-sectional view taken along line XVI-XVI in FIG. 13.

FIGS. 14, 15 and 16 are cross-sectional views of one of the swirl flow suppressors 26b, and FIG. 14 is a cross-sectional view of a section of the swirl flow suppressor 26b, which is located on the radially outer side of the cross-section shown in FIG. 15 in the radial direction Kc1. FIG. 15 is a cross-sectional view of a section of the swirl flow suppressor 26b, which is located on the radially outer side of the cross-section shown in FIG. 16 in the radial direction Kc1.

According to the present embodiment described above, the dimension dDa of each of the swirl flow suppressors 26b measured in the rotational direction Ka1 increases as the swirl flow suppressor 26b extends from the radially inner side toward the radially outer side in the radial direction Kc1. The dimension dDa is a dimension between the end surface 275A and the end surface 275B of each of the swirl flow suppressors 26b.

The end surface 275A is an end surface of the swirl flow suppressor 26b, which faces the other side in the rotational direction Ka1. The end surface 275B is an end surface of the swirl flow suppressor 26b, which faces the one side in the rotational direction Ka1.

Therefore, as compared to the first embodiment described above, the pressure loss, which occurs when the airflow passes through the sub-passages 130a, increases from the radially inner side toward the radially outer side in the radial direction Kc1.

Accordingly, as compared to the first embodiment described above, the amount of the airflow, which flows on the radially outer side in the radial direction Kc1 in the sub-passages 130a, can be reduced.

As a result, the noise, which is generated when the swirl flow flowing on the radially outer side in the radial direction Kc1 collides with the swirl flow suppressors 26b, can be reduced. Accordingly, it is possible to provide the blower device 100 configured to reduce the noise.

Fifth Embodiment

In the first embodiment described above, the example is described in which each of the swirl flow suppressors 26b extends in the radial direction Kc1.

In place of this, in the fifth embodiment, an example is described, with reference to FIG. 17, in which each of the swirl flow suppressors 26b is formed to extend toward the one side in the rotational direction Ka1 as the swirl flow suppressor 26b extends from the radially inner side toward the radially outer side in the radial direction Kc1.

FIG. 17 is a cross-sectional view of the flow straightener mechanism 26 of the present embodiment, taken along a virtual plane that is perpendicular to the fan axis CL1. Dotted lines in FIG. 17 indicate a comparative example in which a plurality of swirl flow suppressors 26b are formed to extend linearly in the radial direction Kc1.

In the present embodiment, the swirl flow suppressors 26b are each formed in a backwardly extending shape such that the swirl flow suppressor 26b advances toward the one side in the rotational direction Ka1 as the swirl flow suppressor 26b extends from the radially inner side toward the radially outer side in the radial direction Kc1. In the present embodiment, in each of the swirl flow suppressors 26b, an end surface (serving as an another-side end portion) 270A is formed on the other side of the swirl flow suppressor 26b in the rotational direction Ka1 of the blower fan 201 and is elongated along the radial direction Kc1.

The swirl flow suppressors 26b are each formed such that the end surface 270A of each of the swirl flow suppressors 26b extends toward the one side in the rotational direction Ka1 as the end surface 270A extends from the radially inner side toward the radially outer side in the radial direction Kc1. Therefore, compared with the comparative example, in which the swirl flow suppressors 26b are formed to extend linearly from the radially inner side toward the radially outer side in the radial direction Kc1, the flow velocity of the swirl flow, which collides with the swirl flow suppressors 26b, can be reduced.

As a result, the noise, which is generated when the air blown from the blower fan 201 collides with the swirl flow suppressors 26b, can be reduced. Accordingly, it is possible to provide the blower device 100 configured to reduce the noise.

An end part of each end surface 270A, which is located radially outermost in the radial direction Kc1 in the end surface 270A, is defined as a radially outer end part 273. An end part of each end surface 270A, which is located radially innermost in the radial direction Kc1 in the end surface 270A, is defined as a radially inner end part 274.

Here, a distance between the radially outer end part 273 and the radially inner end part 274 measured in the rotational direction Ka1 is defined as a rotational distance dDk.

The swirl flow suppressors 26b of the present embodiment include at least two swirl flow suppressors 26b, the rotational distances dDk of which are different from each other. For example, the swirl flow suppressors 26b are configured such that the rotational distances dDk of all of the swirl flow suppressors 26b are different from each other.

As a result, the frequencies of the noise, which is generated when the swirl flow collides with the swirl flow suppressors 26b, are dispersed. Accordingly, discomfort caused by the noise to the user can be reduced.

Sixth Embodiment

In the sixth embodiment, an example is described, with reference to FIG. 18, in which a reinforcing ring 29 is added to the flow straightener mechanism 26 of the fifth embodiment. FIG. 18 is a cross-sectional view of the flow straightener mechanism 26 of the present embodiment, taken along a virtual plane that is perpendicular to the fan axis CL1.

In the flow straightener mechanism 26 of the present embodiment, all of the swirl flow suppressors 26b are coupled together by the reinforcing ring 29. The reinforcing ring 29 is shaped in a ring form that is centered on the fan axis CL1. As a result, the strength of the swirl flow suppressors 26b can be improved.

Seventh Embodiment

In the seventh embodiment, an example is described, with reference to FIG. 19, in which each of the swirl flow suppressors 26b of the flow straightener mechanism 26 of the first embodiment is formed in a curved shape.

As shown in FIG. 19, each of the swirl flow suppressors 26b is formed in a curved shape that is convex in an inclined direction Kd1 toward the one side in the rotational direction Ka1. The inclined direction Kd1 is an intersecting direction that intersects both the rotational direction Ka1 and the fan axial direction DRa. Specifically, the inclined direction Kd1 is an intersecting direction that is perpendicular to both the rotational direction Ka1 and the fan axial direction DRa.

The inclined direction Kd1 is defined such that the inclined direction Kd1 is directed from the other side toward the one side in the rotational direction Ka1 as the inclined direction Kd1 proceeds from the other side toward the one side in the fan axial direction DRa.

In each of the swirl flow suppressors 26b, an end surface 270B is provided on one side of the swirl flow suppressor 26b in the inclined direction Kd1 which corresponds to the one side of the swirl flow suppressor 26b in the rotational direction Ka1. In each of the swirl flow suppressors 26b, an end surface 270A is provided on the other side of the swirl flow suppressor 26b in the inclined direction Kd1 which corresponds to the other side of the swirl flow suppressor 26b in the rotational direction Ka1.

The end surface 270B and the end surface 270A are each formed in a curved shape that is convex in the inclined direction Kd1 toward the one side in the rotational direction Ka1.

According to the present embodiment described above, each of the swirl flow suppressors 26b is formed such that each of the end surfaces 270B, 270A of the swirl flow suppressor 26b extends toward the other side in the fan axial direction DRa as the end surface 270B, 270A extends from the radially inner side toward the radially outer side in the radial direction Kc1 about the fan axis CL1. The end surface 270A of each of the swirl flow suppressors 26b is formed in the curved shape that is convex in the inclined direction Kd1 toward the one side in the rotational direction Ka1.

The end surface 270B of each of the swirl flow suppressors 26b is formed in the curved shape that is convex in the inclined direction Kd1 toward the one side in the rotational direction Ka1. Accordingly, the pressure loss, which occurs as the airflow passes through the flow straightener mechanism 26, can be reduced. Accordingly, it is possible to provide the blower device 100 configured to further reduce the noise.

Eighth Embodiment

In the first embodiment described above, there is described the example in which each of the swirl flow suppressors 26b is formed to extend toward the other side in the fan axial direction DRa as the swirl flow suppressor 26b extends from the radially inner side toward the radially outer side in the radial direction Kc1.

In place of this, in the eighth embodiment, an example is described, with reference to FIGS. 20, 21 and 22, in which each of the swirl flow suppressors 26b is formed to extend toward the one side in the fan axial direction DRa as the swirl flow suppressor 26b extends from the radially inner side toward the radially outer side in the radial direction Kc1.

FIG. 20 is a cross-sectional view of the flow straightener mechanism 26 of the present embodiment, taken along a virtual plane including the fan axis CL1. Dotted lines in FIG. 20 indicate a comparative example in which a plurality of swirl flow suppressors 26b are formed to extend linearly in the radial direction Kc1.

FIG. 21 is a view showing the cover 26a and one of the swirl flow suppressors 26b in the flow straightener mechanism 26 of the present embodiment, and also showing a flow velocity Za of the air flowing from the sub-passages 130a toward the other side in the fan axial direction DRa.

FIG. 22 is a diagram showing a flow velocity Za of the air flowing from the sub-passages 130a toward the other side in the fan axial direction DRa in a comparative example, in which the swirl flow suppressors 26b extend linearly from the radially inner side toward to the radially outer side in the radial direction Kc1.

Each of the swirl flow suppressors 26b can suppress the swirl flow and thereby generate the airflow that flows toward the other side in the fan axial direction DRa.

In the swirl flow, the flow velocity of the air increases from the radially inner side toward the radially outer side in the radial direction Kc1. Accordingly, the swirl flow suppressors 26b of the present embodiment can generate the airflow, in which the flow velocity of the air increases from the radially inner side toward the radially outer side in the radial direction Kc1.

According to the present embodiment, the swirl flow suppressors 26b are each formed in a forwardly inclined shape such that the swirl flow suppressor 26b extends toward the one side in the fan axial direction DRa as the swirl flow suppressor 26b extends from the radially inner side toward the radially outer side in the radial direction Kc1. The end surface 270 of each of the swirl flow suppressors 26b is formed such that the end surface 270 extends toward the one side in the fan axial direction DRa as the end surface 270 extends from the radially inner side toward the radially outer side in the radial direction Kc1.

Accordingly, in the through-passage 130 located on the downstream side of the swirl flow suppressors 26b in the airflow direction, a difference between the flow velocity of the air flowing on the radially outer side and the flow velocity of the air flowing on the radially inner side can be made larger than in the comparative example described above.

Accordingly, in the through-passage 130 (in each of the sub-passages 130a), an airflow is generated to flow from the radially outer side toward the radially central side about the fan axis CL1, as indicated by an arrow Qz. Thus, it is possible to reduce the amount of the airflow, which flows from the through-passage 130 (that is, from the sub-passages 130a) toward the other side in the fan axial direction DRa.

Accordingly, it is possible to reduce the noise, which is generated when the air flows from the through-passage 130 toward the other side in the fan axial direction DRa. Accordingly, it is possible to provide the blower device 100 configured to reduce the noise.

In the present embodiment, similarly to the first embodiment described above, as shown in FIG. 20, in each of the swirl flow suppressors 26b, the end surface 270 is formed on the one side of the swirl flow suppressor 26b in the fan axial direction DRa and is elongated along the radial direction Kc1.

An end part of each end surface 270, which is located radially outermost in the radial direction Kc1 in the end surface 270, is defined as a radially outer end part 271.

An end part of each end surface 270, which is located radially innermost in the radial direction Kc1 in the end surface 270, is defined as a radially inner end part 272. Here, a distance between the radially outer end part 271 and the radially inner end part 272 measured in the fan axial direction DRa is defined as an axial distance dDR.

The swirl flow suppressors 26b of the present embodiment include at least two swirl flow suppressors 26b, the axial distances dDR of which are different from each other. For example, the swirl flow suppressors 26b are configured such that the axial distances dDR of all of the swirl flow suppressors 26b are different from each other.

As a result, the frequencies of noise, which is generated when the swirl flow is guided by the swirl flow suppressors 26b, are dispersed. Accordingly, discomfort caused by the noise to the user can be reduced.

Ninth Embodiment

In the ninth embodiment, with reference to FIG. 23, an example will be described in which each of the swirl flow suppressors 26b of the eighth embodiment is formed in a curved shape that is convex toward the other side in the fan axial direction DRa.

FIG. 23 is a cross-sectional view of the flow straightener mechanism 26 of the present embodiment, taken along a virtual plane that is parallel to the fan axis CL1.

According to the present embodiment described above, each of the swirl flow suppressors 26b is formed in the curved shape that is convex toward the other side in the fan axial direction DRa. Thus, it is possible to reduce the pressure loss, which occurs when the air blown from the blower fan 201 passes through the flow straightener mechanism 26. Accordingly, it is possible to provide the blower device 100 configured to further reduce the noise.

Tenth Embodiment

In the fifth embodiment described above, there is described the example in which the end surface 270A of each of the swirl flow suppressors 26b is formed to extend toward the one side in the rotational direction Ka1 as the end surface 270A extends from the radially inner side toward the radially outer side in the radial direction Kc1.

In place of this, in the tenth embodiment, an example is described, with reference to FIG. 24, in which the end surface 270A of each of the swirl flow suppressors 26b is formed to extend toward the other side in the rotational direction Ka1 as the end surface 270A extends from the radially inner side toward the radially outer side in the radial direction Kc1.

FIG. 24 is a cross-sectional view of the flow straightener mechanism 26 of the present embodiment, taken along a virtual plane that is perpendicular to the fan axis CL1. Dotted lines in FIG. 24 indicate a comparative example in which a plurality of swirl flow suppressors 26b are formed to extend linearly in the radial direction Kc1.

Each of the swirl flow suppressors 26b can suppress the swirl flow and thereby generate the airflow that flows toward the other side in the fan axial direction DRa.

In the swirl flow, the flow velocity of the air increases from the radially inner side toward the radially outer side in the radial direction Kc1. Accordingly, the swirl flow suppressors 26b of the present embodiment can generate the airflow, in which the flow velocity of the air increases from the radially inner side toward the radially outer side in the radial direction Kc1.

In the present embodiment, the swirl flow suppressors 26b are each formed such that the end surface 270A of each of the swirl flow suppressors 26b extends toward the other side in the rotational direction Ka1 as the end surface 270A extends from the radially inner side toward the radially outer side in the radial direction Kc1.

Accordingly, in the through-passage 130 located on the downstream side of the swirl flow suppressors 26b in the airflow direction, a difference between the flow velocity of the air flowing on the radially outer side and the flow velocity of the air flowing on the radially inner side can be made larger than in the comparative example described above.

Accordingly, similar to the eighth embodiment, in each of the sub-passages 130a, an airflow is generated to flow from the radially outer side toward the radially central side around the fan axis CL1. Thus, it is possible to reduce the amount of the airflow, which flows from the through-passage 130 (that is, from the sub-passages 130a) toward the other side in the fan axial direction DRa.

Accordingly, it is possible to reduce the noise, which is generated when the air flows from the through-passage 130 toward the other side in the fan axial direction DRa. Accordingly, it is possible to provide the blower device 100 configured to reduce the noise.

In the present embodiment, similar to the fifth embodiment, in each of the swirl flow suppressors 26b, an end surface (serving as an another-side end portion) 270A is formed on the other side of the swirl flow suppressor 26b in the rotational direction Ka1 of the blower fan 201 and is elongated along the radial direction Kc1.

An end part of each end surface 270A, which is located radially outermost in the radial direction Kc1 in the end surface 270A, is defined as a radially outer end part 273. An end part of each end surface 270A, which is located radially innermost in the radial direction Kc1 in the end surface 270A, is defined as a radially inner end part 274.

Here, a distance between the radially outer end part 273 and the radially inner end part 274 measured in the rotational direction Ka1 is defined as a rotational distance dDk.

The swirl flow suppressors 26b of the present embodiment include at least two swirl flow suppressors 26b, the rotational distances dDk of which are different from each other. For example, the swirl flow suppressors 26b are configured such that the rotational distances dDk of all of the swirl flow suppressors 26b are different from each other.

As a result, similar to the fifth embodiment, the frequencies of the noise, which is generated when the swirl flow collides with the swirl flow suppressors 26b, are dispersed. Accordingly, discomfort caused by the noise to the user can be reduced.

Eleventh Embodiment

In the eleventh embodiment, with reference to FIG. 25, an example will be described in which each of the swirl flow suppressors 26b of the flow straightener mechanism 26 of the tenth embodiment is formed in a curved shape that is convex toward the one side in the rotational direction Ka1.

FIG. 25 is a cross-sectional view of the flow straightener mechanism 26 of the present embodiment, taken along a virtual plane that is perpendicular to the fan axis CL1.

According to the present embodiment described above, each of the swirl flow suppressors 26b is formed in the curved shape that is convex toward the one side in the rotational direction Ka1. Accordingly, the pressure loss, which occurs as the airflow passes through the flow straightener mechanism 26, can be reduced.

Accordingly, it is possible to provide the blower device 100 configured to further reduce the noise.

Twelfth Embodiment

In the fourth embodiment, there is described the example in which the dimension of each of the swirl flow suppressors 26b measured in the rotational direction Ka1 increases as the swirl flow suppressor 26b extends from the radially inner side toward the radially outer side in the radial direction Kc1.

In place of this, in the twelfth embodiment, an example will be described with reference to FIGS. 26, 27, 28 and 29, in which the dimension dDa of each of the swirl flow suppressors 26b measured in the rotational direction Ka1 decreases as the swirl flow suppressor 26b extends from the radially inner side toward the radially outer side in the radial direction Kc1.

FIG. 26 is a cross-sectional view of the flow straightener mechanism 26 of the present embodiment taken along a virtual plane perpendicular to the fan axis CL1. FIG. 27 is a cross-sectional view taken along line XXVII-XXVII in FIG. 26. FIG. 28 is a cross-sectional view taken along line XXVIII-XXVIII in FIG. 26, and FIG. 29 is a cross-sectional view taken along line XXIX-XXIX in FIG. 26. In FIG. 26, the same reference numerals as those used in FIG. 13 denote the same components, and a detailed description thereof is omitted.

FIGS. 27, 28 and 29 are cross-sectional views of one of the swirl flow suppressors 26b, and FIG. 27 is a cross-sectional view of a section of the swirl flow suppressor 26b, which is located on the radially outer side of the cross-section shown in FIG. 28 in the radial direction Kc1. FIG. 28 is a cross-sectional view of a section of the swirl flow suppressor 26b, which is located on the radially outer side of the cross-section shown in FIG. 29 in the radial direction Kc1.

According to the present embodiment described above, each of the swirl flow suppressors 26b can suppress the swirl flow and thereby generate the airflow that flows toward the other side in the fan axial direction DRa.

In the swirl flow, the flow velocity of the air increases from the radially inner side toward the radially outer side in the radial direction Kc1. Accordingly, the swirl flow suppressors 26b of the present embodiment can generate the airflow, in which the flow velocity of the air increases from the radially inner side toward the radially outer side in the radial direction Kc1.

The dimension dDa of each of the swirl flow suppressors 26b measured in the rotational direction Ka1 decreases as the swirl flow suppressor 26b extends from the radially inner side toward the radially outer side in the radial direction Kc1. The dimension dDa is a dimension between the end surface 275A and the end surface 275B of each of the swirl flow suppressors 26b measured in the rotational direction Ka1. Therefore, the dimension of each of the sub-passages 130a measured in the rotational direction Ka1 decreases as the sub-passage 130a extends from the radially inner side toward the radially outer side in the radial direction Kc1.

Therefore, the pressure loss, which occurs when the airflow passes through the sub-passage 130a, decreases from the radially inner side toward the radially outer side in the radial direction Kc1.

Accordingly, in the through-passage 130 located on the downstream side of the swirl flow suppressors 26b in the airflow direction, a difference between the flow velocity of the air flowing on the radially outer side and the flow velocity of the air flowing on the radially inner side can be made larger than in a comparative example described below. The comparative example refers to an example in which a plurality of swirl flow suppressors 26b are formed to extend linearly in the radial direction Kc1.

As a result, similarly to the above-described eighth and tenth embodiments, it is possible to generate the airflow that flows from the radially outer side toward the radially central side in the radial direction Kc1 within the sub-passages 130a, on the downstream side of the swirl flow suppressors 26b.

Thus, it is possible to reduce the amount of the airflow, which flows from the sub-passages 130a toward the other side in the axial direction. Accordingly, it is possible to reduce the noise, which is generated when the air flows through the sub-passages 130a.

Thirteenth Embodiment

In the flow straightener mechanism 26 of the thirteenth embodiment, with reference to FIGS. 30 and 31, an example will be described in which a mechanism is used that combines the swirl flow suppressors 26b of the tenth embodiment, each of which has the forwardly extending shape, and the swirl flow suppressors 26b of the eighth embodiment, each of which has the forwardly inclined shape.

FIGS. 30 and 31 are perspective views showing one of the swirl flow suppressors 26b of the flow straightener mechanism 26, as viewed from the other side in the rotational direction Ka1. Dotted lines in FIG. 30 indicate a comparative example in which one of the swirl flow suppressors 26b is formed to extend linearly in the radial direction Kc1. Dotted lines in FIG. 31 indicate a comparative example in which one of the swirl flow suppressors 26b has an axial position in the fan axial direction DRa that remains constant along the radial direction Kc1.

The swirl flow suppressors 26b of the present embodiment are each formed such that the end surface 270A of each of the swirl flow suppressors 26b extends toward the other side in the rotational direction Ka1 as the end surface 270A extends from the radially inner side toward the radially outer side in the radial direction Kc1, like in the tenth embodiment.

Accordingly, like in the tenth embodiment, it is possible to reduce the noise, which is generated when the air flows from the sub-passages 130a toward the other side in the fan axial direction DRa.

The swirl flow suppressors 26b of the present embodiment are each formed such that the end surface 270 of each of the swirl flow suppressors 26b extends toward the one side in the fan axial direction DRa as the end surface 270 extends from the radially inner side toward the radially outer side in the radial direction Kc1, like in the eighth embodiment. Accordingly, like in the eighth embodiment, it is possible to reduce the noise, which is generated when the air flows from the sub-passages 130a toward the other side in the fan axial direction DRa.

According to the present embodiment described above, by combining the tenth embodiment and the eighth embodiment, the noise can be reduced even further.

Fourteenth Embodiment

In the flow straightener mechanism 26 of the fourteenth embodiment, with reference to FIGS. 32 and 33, an example will be described in which a mechanism is used that combines the swirl flow suppressors 26b of the fifth embodiment, each of which has the backwardly extending shape, and the swirl flow suppressors 26b of the eighth embodiment, each of which has the forwardly inclined shape.

FIGS. 32 and 33 are perspective views showing one of the swirl flow suppressors 26b of the flow straightener mechanism 26, as viewed from the other side in the rotational direction Ka1. Dotted lines in FIG. 33 indicate a comparative example in which one of the swirl flow suppressors 26b is formed to extend linearly in the radial direction Kc1. Dotted lines in FIG. 32 indicate a comparative example in which one of the swirl flow suppressors 26b has an axial position in the fan axial direction DRa that remains constant along the radial direction Kc1.

The swirl flow suppressors 26b of the present embodiment are each formed such that the end surface 270 of each of the swirl flow suppressors 26b extends toward the one side in the fan axial direction DRa as the end surface 270 extends from the radially inner side toward the radially outer side in the radial direction Kc1, like in the eighth embodiment.

Accordingly, like in the eighth embodiment, it is possible to reduce the noise, which is generated when the air flows from the sub-passages 130a toward the other side in the fan axial direction DRa.

The swirl flow suppressors 26b of the present embodiment are each formed such that the end surface 270A of each of the swirl flow suppressors 26b extends toward the one side in the rotational direction Ka1 as the end surface 270A extends from the radially inner side toward the radially outer side in the radial direction Kc1, like in the fifth embodiment.

Therefore, like in the fifth embodiment, the noise, which is generated when the air blown from the blower fan 201 collides with the swirl flow suppressors 26b, can be reduced.

According to the present embodiment described above, by combining the fifth embodiment and the eighth embodiment, the noise can be reduced even further.

Fifteenth Embodiment

In the flow straightener mechanism 26 of the present embodiment, with reference to FIGS. 34 and 35, an example will be described in which a mechanism is used that combines the swirl flow suppressors 26b of the first embodiment, each of which has the backwardly inclined shape, and the swirl flow suppressors 26b of the tenth embodiment, each of which has the forwardly extending shape.

FIGS. 34 and 35 are perspective views showing one of the swirl flow suppressors 26b of the flow straightener mechanism 26, as viewed from the other side in the rotational direction Ka1. Dotted lines in FIG. 34 indicate a comparative example in which one of the swirl flow suppressors 26b is formed to extend linearly in the radial direction Kc1. Dotted lines in FIG. 35 indicate a comparative example in which one of the swirl flow suppressors 26b has an axial position in the fan axial direction DRa that remains constant along the radial direction Kc1.

Like in the first embodiment, the end surface 270 of each of the swirl flow suppressors 26b of the present embodiment is formed to extend toward the other side in the fan axial direction DRa as the end surface 270 extends from the radially inner side toward the radially outer side in the radial direction Kc1 about the fan axis CL1. Therefore, like in the first embodiment, the noise, which is generated when the air blown from the blower fan 201 collides with the swirl flow suppressors 26b, can be reduced.

The swirl flow suppressors 26b of the present embodiment are each formed such that the end surface 270A of each of the swirl flow suppressors 26b extends toward the other side in the rotational direction Ka1 as the end surface 270A extends from the radially inner side toward the radially outer side in the radial direction Kc1, like in the tenth embodiment. Accordingly, like in the tenth embodiment, it is possible to reduce the noise, which is generated when the air flows from the sub-passages 130a toward the other side in the fan axial direction DRa.

According to the present embodiment described above, by combining the first embodiment and the tenth embodiment, the noise can be reduced even further.

Sixteenth Embodiment

In the flow straightener mechanism 26 of the present embodiment, with reference to FIGS. 36 and 37, an example will be described in which a mechanism is used that combines the swirl flow suppressors 26b of the first embodiment, each of which has the backwardly inclined shape, and the swirl flow suppressors 26b of the fifth embodiment, each of which has the backwardly extending shape.

FIGS. 36 and 37 are perspective views showing one of the swirl flow suppressors 26b of the flow straightener mechanism 26, as viewed from the other side in the rotational direction Ka1. Dotted lines in FIG. 36 indicate a comparative example in which one of the swirl flow suppressors 26b is formed to extend linearly in the radial direction Kc1. Dotted lines in FIG. 37 indicate a comparative example in which one of the swirl flow suppressors 26b has an axial position in the fan axial direction DRa that remains constant along the radial direction Kc1.

The swirl flow suppressors 26b of the present embodiment are each formed in the backwardly extending shape such that the end surface 270A of each of the swirl flow suppressors 26b extends toward the one side in the rotational direction Ka1 as the end surface 270A extends from the radially inner side toward the radially outer side in the radial direction Kc1, like in the fifth embodiment. Therefore, like in the fifth embodiment, the noise, which is generated when the air blown from the blower fan 201 collides with the swirl flow suppressors 26b, can be reduced.

Like in the first embodiment, the end surface 270 of each of the swirl flow suppressors 26b of the present embodiment is formed to extend toward the other side in the fan axial direction DRa as the end surface 270 extends from the radially inner side toward the radially outer side in the radial direction Kc1 about the fan axis CL1.

Therefore, like in the first embodiment, the noise, which is generated when the air blown from the blower fan 201 collides with the swirl flow suppressors 26b, can be reduced.

According to the present embodiment described above, by combining the first embodiment and the fifth embodiment, the noise can be reduced even further.

Other Embodiments

• • (1) In the first to sixteenth embodiments described above, there is described the example in which the blower device 100 of the present disclosure is applied to the vehicle air-conditioning unit 10.

However, instead of this, the blower device 100 of the present disclosure may be applied to various devices such as stationary air-conditioning units other than the vehicle air-conditioning unit 10.

• • (2) In the fourth embodiment described above, there is described the example in which the dimension dDa of each of the swirl flow suppressors 26b measured in the rotational direction Ka1 increases as the swirl flow suppressor 26b extends from the radially inner side toward the radially outer side in the radial direction Kc1.

However, instead of this, in the first to third embodiments and the fourth to sixteenth embodiments described above, the dimension dDa of each of the swirl flow suppressors 26b measured in the rotational direction Ka1 may be set to increase from the radially inner side toward the radially outer side in the radial direction Kc1.

• • (3) In the twelfth embodiment described above, there is described the example in which the dimension dDa of each of the swirl flow suppressors 26b measured in the rotational direction Ka1 decreases as the swirl flow suppressor 26b extends from the radially inner side toward the radially outer side in the radial direction Kc1.

However, instead of this, in the first to eleventh embodiments and the twelfth to sixteenth embodiments described above, the dimension dDa of each of the swirl flow suppressors 26b measured in the rotational direction Ka1 may be set to decrease from the radially inner side toward the radially outer side in the radial direction Kc1.

• • (4) In the third embodiment described above, there is described the example in which the acute angle θ2, which is defined between the end surface 27a and the virtual plane Sa in each of the swirl flow suppressors 26b of the first embodiment, decreases from the radially inner side toward the radially outer side in the radial direction Kc1.

However, instead of this, in each of the swirl flow suppressors 26b in the second embodiment and the fourth to sixteenth embodiments described above, the acute angle θ2, which is defined between the end surface 27a and the virtual plane Sa, may be set to decrease from the radially inner side toward the radially outer side in the radial direction Kc1.

In each of the swirl flow suppressors 26b in the second embodiment and the fourth to sixteenth embodiments described above, the acute angle θ3, which is defined between the end surface 27b and the virtual plane Sa, may be set to decrease from the radially inner side toward the radially outer side in the radial direction Kc1.

• • (5) In the seventh embodiment described above, there is described the example in which each of the swirl flow suppressors 26b in the first embodiment is formed in the curved shape that is convex in the inclined direction Kd1 toward the one side in the rotational direction Ka1.

However, instead of this, in the second to sixth embodiments and the eighth to sixteenth embodiments described above, each of the swirl flow suppressors 26b may be formed in the curved shape that is convex in the inclined direction Kd1 toward the one side in the rotational direction Ka1.

• • (6) In the first embodiment and the eighth embodiment described above, there is described the example in which the swirl flow suppressors 26b include the at least two swirl flow suppressors 26b, the axial distances dDR of which are different from each other.

However, instead of this, in the second to seventh embodiments and the ninth to sixteenth embodiments described above, the swirl flow suppressors 26b may include at least two swirl flow suppressors 26b, the axial distances dDR of which are different from each other.

For example, in the second to seventh embodiments and the ninth to sixteenth embodiments described above, all of the swirl flow suppressors 26b may have different axial distances dDR which are different from each other.

• • (7) In the first embodiment described above, there is described the example in which the swirl flow suppressors 26b are arranged in the circumferential direction such that the two or more of the intervals Kn are different from each other.

However, instead of this, in the second to sixteenth embodiments described above, the swirl flow suppressors 26b of the flow straightener mechanism 26 may be arranged in the circumferential direction such that two or more of the intervals Kn are different from each other. For example, the flow straightener mechanism 26 may be configured such that the intervals Kn of the eight sub-passages 130a are different from each other.

• • (8) In the first embodiment described above, there is described the example in which the radially outer end part of each of the swirl flow suppressors 26b, which faces the outer side in the radial direction Kc1, is joined to the inner wall 12a, and the radially inner end part of each of the swirl flow suppressors 26b, which faces the inner side in the radial direction Kc1, is joined to the cover 26a. However, instead of this, the following alternatives (a) and (b) may be adopted.
  • (a) The swirl flow suppressors 26b may be configured such that the radially outer end part of each of the swirl flow suppressors 26b, which faces the outer side in the radial direction Kc1, is joined to the inner wall 12a, and the radially inner end part of each of the swirl flow suppressors 26b, which faces the inner side in the radial direction Kc1, is not joined to the cover 26a.
  • (b) The swirl flow suppressors 26b may be configured such that the radially outer end part of each of the swirl flow suppressors 26b, which faces the outer side in the radial direction Kc1, is not joined to the inner wall 12a, and the radially inner end part of each of the swirl flow suppressors 26b, which faces the inner side in the radial direction Kc1, is joined to the cover 26a.
  • (9) In the first and eighth embodiments described above, there is described the example in which with respect to the end surface 270 of each of the swirl flow suppressors 26b, the distance between the radially outer end part 271 and the radially inner end part 272 measured in the fan axial direction DRa is defined as the axial distance dDR.

However, instead of this, the following alternative may be adopted. That is, in each of the swirl flow suppressors 26b, an another-side end portion of the swirl flow suppressor 26b, which faces the other side in the fan axial direction DRa and is elongated along the radial direction Kc1, is defined as an another-side end surface.

An end part of the another-side end surface of each swirl flow suppressor 26b, which is located radially innermost in the radial direction in the another-side end surface, is defined as a radially inner end part. An end part of the another-side end surface of each swirl flow suppressor 26b, which is located radially outermost in the radial direction in the another-side end surface, is defined as a radially outer end part. Here, a distance between the radially outer end part and the radially inner end part measured in the fan axial direction is defined as an axial distance dDR.

• • (10) In the fifth and tenth embodiments described above, there is described the example in which with respect to the end surface 270A of each of the swirl flow suppressors 26b, the distance between the radially outer end part 273 and the radially inner end part 274 measured in the rotational direction Ka1 is defined as the rotational distance dDk.

However, instead of this, the following alternative may be adopted. That is, in each of the swirl flow suppressors 26b, a one-side end portion of the swirl flow suppressor 26b, which faces the one side in the rotational direction Ka1 of the blower fan 201 and is elongated along the radial direction Kc1, is defined as a one-side end surface.

An end part of the one-side end surface of each swirl flow suppressor 26b, which is located radially outermost in the radial direction Kc1 in the one-side end surface, is defined as a radially outer end part. Among the end surfaces 270A, an end part of the one-side end surface, which is located radially innermost in the radial direction Kc1 in the one-side end surface, is defined as a radially inner end part.

Here, a distance between the radially outer end part and the radially inner end part measured in the rotational direction Ka1 is defined as a rotational distance dDk.

• • (11) In the first embodiment described above, there is described the example in which the flow straightener mechanism 26 is configured such that, when the light is projected from the light source 300 onto the flow straightener mechanism 26 from the one side in the fan axial direction DRa, shadows cast by the swirl flow suppressors 26b onto the wall 301 are offset from each other.

Similarly, in the second to sixteenth embodiments described above, the flow straightener mechanism 26 may be configured such that when the light is projected from the light source 300 onto the flow straightener mechanism 26 from the one side in the fan axial direction DRa, shadows cast by the swirl flow suppressors 26b onto the wall 301 are offset from each other.

• • (12) In the fourth embodiment described above, there is described the example in which the swirl flow suppressors 26b are configured such that the dimension (i.e., the dimension dDa) measured between the end surfaces 275A, 275B of the swirl flow suppressor 26b in the rotational direction Ka1 increases as the swirl flow suppressor 26b extends from the radially inner side toward the radially outer side in the radial direction Kc1.

However, the present invention is not limited to this, and the swirl flow suppressors 26b are not necessarily required to define the dimension dDa in the rotational direction Ka1 as the dimension between the end surfaces 275A, 275B, as long as the dimension dDa of each of the swirl flow suppressors 26b in the rotational direction Ka1 increases from the radially inner side toward the radially outer side in the radial direction Kc1. The same applies to the twelfth embodiment described above.

• • (12) In the fourth embodiment described above, there is described the example in which the dimension dDa of each of the swirl flow suppressors 26b measured in the rotational direction Ka1 increases as the swirl flow suppressor 26b extends from the radially inner side toward the radially outer side in the radial direction Kc1. In addition, in the fourth embodiment described above, the swirl flow suppressors 26b may be configured such that each of the swirl flow suppressors 26b has an identical shape. Alternatively, two or more of the swirl flow suppressors 26b may have different shapes which are different from each other.
  • (13) In the twelfth embodiment described above, there is described the example in which the dimension dDa of each of the swirl flow suppressors 26b measured in the rotational direction Ka1 decreases as the swirl flow suppressor 26b extends from the radially inner side toward the radially outer side in the radial direction Kc1. In addition, in the twelfth embodiment described above, the swirl flow suppressors 26b may be configured such that each of the swirl flow suppressors 26b has an identical shape. Alternatively, two or more of the swirl flow suppressors 26b may have different shapes which are different from each other.
  • (14) The present disclosure is not limited to the embodiments described above. Further, the above embodiments are not unrelated to each other and can be appropriately combined unless the combination is clearly impossible. Needless to say, in each of the above-described embodiments, the elements of the embodiment are not necessarily essential except when it is clearly indicated that they are essential and when they are clearly considered to be essential in principle. In each of the embodiments described above, when a numerical value such as the number, numerical value, amount, range or the like of the constituent elements of the embodiment is mentioned, the present disclosure should not be limited to such a numerical value unless it is clearly stated that it is essential and/or it is required in principle. In each of the embodiments described above, when the shape, the positional relationship or the like of the constituent elements of the embodiment are mentioned, the present disclosure should not be limited the shape, the positional relationship or the like unless it is clearly stated that it is essential and/or it is required in principle.

(Various Aspects)

(Aspect 1)

According to aspect 1 of the present disclosure, there is provided a blower device including:

• • an air conditioning case that has an inner wall, wherein the inner wall forms an air passage which is configured to conduct air;
  • a blower fan that is disposed in the air passage, wherein a direction, in which an axis of the blower fan extends, is defined as an axial direction, and the blower fan is configured to rotate about the axis to draw in the air from one side in the axial direction and to blow the air out toward a radially outer side in a radial direction about the axis;
  • a cover that is disposed on another side in the axial direction with respect to the blower fan in the air passage and is formed to cover the blower fan from the another side in the axial direction, wherein the cover forms, between the cover and the inner wall, a through-passage that is configured to conduct the air blown out from the blower fan toward the another side in the axial direction; and
  • at least one swirl flow suppressor that is disposed in the through-passage and is elongated along the radial direction, wherein the at least one swirl flow suppressor is configured to suppress a swirl flow of the air generated by rotation of the blower fan, and thereby to generate an airflow that flows toward the another side in the axial direction, wherein:
  • a one-side end portion of the at least one swirl flow suppressor, which faces the one side in the axial direction, is formed to extend toward the another side in the axial direction as the one-side end portion extends from a radially inner side toward the radially outer side in the radial direction.

(Aspect 2)

According to aspect 2, there is provided a blower device including:

• • an air conditioning case that has an inner wall, wherein the inner wall forms an air passage which is configured to conduct air;
  • a blower fan that is disposed in the air passage, wherein a direction, in which an axis of the blower fan extends, is defined as an axial direction, and the blower fan is configured to rotate about the axis to draw in the air from one side in the axial direction and to blow the air out toward a radially outer side in a radial direction about the axis;
  • a cover that is disposed on another side in the axial direction with respect to the blower fan in the air passage and is formed to cover the blower fan from the another side in the axial direction, wherein the cover forms, between the cover and the inner wall, a through-passage that is configured to conduct the air blown out from the blower fan toward the another side in the axial direction; and
  • at least one swirl flow suppressor that is disposed in the through-passage and is elongated along the radial direction, wherein the at least one swirl flow suppressor is configured to suppress a swirl flow of the air generated by rotation of the blower fan, and thereby to generate an airflow that flows toward the another side in the axial direction, wherein:
  • a one-side end portion of the at least one swirl flow suppressor, which faces the one side in the axial direction, is formed to extend toward the one side in the axial direction as the one-side end portion extends from a radially inner side toward the radially outer side in the radial direction.

(Aspect 3)

According to aspect 3, there is provided the blower device according to aspect 1 or 2, wherein:

• • an end part of the one-side end portion of the at least one swirl flow suppressor, which faces the one side in the axial direction and is located radially innermost in the radial direction in the one-side end portion, is defined as a radially inner end part;
  • an end part of the one-side end portion of the at least one swirl flow suppressor, which faces the one side in the axial direction and is located radially outermost in the radial direction in the one-side end portion, is defined as a radially outer end part;
  • a distance between the radially inner end part and the radially outer end part measured in the axial direction is defined as an axial distance; and
  • the at least one swirl flow suppressor is a plurality of swirl flow suppressors that include two or more swirl flow suppressors, wherein the axial distances of the two or more swirl flow suppressors are different from each other.

(Aspect 4)

According to aspect 4, there is provided a blower device including:

• • an air conditioning case that has an inner wall, wherein the inner wall forms an air passage which is configured to conduct air;
  • a blower fan that is disposed in the air passage, wherein a direction, in which an axis of the blower fan extends, is defined as an axial direction, and the blower fan is configured to rotate toward one side in a rotational direction about the axis to draw in the air from one side in the axial direction and to blow the air out toward a radially outer side in a radial direction about the axis;
  • a cover that is disposed on another side in the axial direction with respect to the blower fan in the air passage and is formed to cover the blower fan from the another side in the axial direction, wherein the cover forms, between the cover and the inner wall, a through-passage that is configured to conduct the air blown out from the blower fan toward the another side in the axial direction; and
  • at least one swirl flow suppressor that is disposed in the through-passage and is elongated along the radial direction, wherein the at least one swirl flow suppressor is configured to suppress a swirl flow of the air generated by rotation of the blower fan, and thereby to generate an airflow that flows toward the another side in the axial direction, wherein:
  • an another-side end portion of the at least one swirl flow suppressor, which faces another side opposite to the one side in the rotational direction, is formed to extend toward the one side in the rotational direction as the another-side end portion extends from a radially inner side toward the radially outer side in the radial direction.

(Aspect 5)

According to aspect 5, there is provided a blower device including:

• • an air conditioning case that has an inner wall, wherein the inner wall forms an air passage which is configured to conduct air;
  • a blower fan that is disposed in the air passage, wherein a direction, in which an axis of the blower fan extends, is defined as an axial direction, and the blower fan is configured to rotate toward one side in a rotational direction about the axis to draw in the air from one side in the axial direction and to blow the air out toward a radially outer side in a radial direction about the axis;
  • a cover that is disposed on another side in the axial direction with respect to the blower fan in the air passage and is formed to cover the blower fan from the another side in the axial direction, wherein the cover forms, between the cover and the inner wall, a through-passage that is configured to conduct the air blown out from the blower fan toward the another side in the axial direction; and
  • at least one swirl flow suppressor that is disposed in the through-passage and is elongated along the radial direction, wherein the at least one swirl flow suppressor is configured to suppress a swirl flow of the air generated by rotation of the blower fan, and thereby to generate an airflow that flows toward the another side in the axial direction, wherein:
  • an another-side end portion of the at least one swirl flow suppressor, which faces another side opposite to the one side in the rotational direction, is formed to extend toward the another side in the rotational direction as the another-side end portion extends from a radially inner side toward the radially outer side in the radial direction.

(Aspect 6)

According to aspect 6, there is provided the blower device according to aspect 4 or 5, wherein:

• • an end part of the another-side end portion of the at least one swirl flow suppressor, which faces the another side in the rotational direction and is located radially innermost in the radial direction in the another-side end portion, is defined as a radially inner end part;
  • an end part of the another-side end portion of the at least one swirl flow suppressor, which faces the another side in the rotational direction and is located radially outermost in the radial direction in the another-side end portion, is defined as a radially outer end part;
  • a distance between the radially inner end part and the radially outer end part measured in the rotational direction is defined as a rotational distance; and
  • the at least one swirl flow suppressor is a plurality of swirl flow suppressors that include two or more swirl flow suppressors, wherein the rotational distances of the two or more swirl flow suppressors are different from each other.

(Aspect 7)

According to aspect 7, there is provided a blower device including:

• • an air conditioning case that has an inner wall, wherein the inner wall forms an air passage which is configured to conduct air;
  • a blower fan that is disposed in the air passage, wherein a direction, in which an axis of the blower fan extends, is defined as an axial direction, and the blower fan is configured to rotate about the axis to draw in the air from one side in the axial direction and to blow the air out toward a radially outer side in a radial direction about the axis;
  • a cover that is disposed on another side in the axial direction with respect to the blower fan in the air passage and is formed to cover the blower fan from the another side in the axial direction, wherein the cover forms, between the cover and the inner wall, a through-passage that is configured to conduct the air blown out from the blower fan toward the another side in the axial direction; and
  • at least one swirl flow suppressor that is disposed in the through-passage and is elongated along the radial direction, wherein the at least one swirl flow suppressor is configured to suppress a swirl flow of the air generated by rotation of the blower fan, and thereby to generate an airflow that flows toward the another side in the axial direction, wherein:
  • a dimension of the at least one swirl flow suppressor, which is measured in a rotational direction of the blower fan, increases as the at least one swirl flow suppressor extends from a radially inner side toward the radially outer side in the radial direction.

(Aspect 8)

According to aspect 8, there is provided a blower device including:

• • an air conditioning case that has an inner wall, wherein the inner wall forms an air passage which is configured to conduct air;
  • a blower fan that is disposed in the air passage, wherein a direction, in which an axis of the blower fan extends, is defined as an axial direction, and the blower fan is configured to rotate about the axis to draw in the air from one side in the axial direction and to blow the air out toward a radially outer side in a radial direction about the axis;
  • a cover that is disposed on another side in the axial direction with respect to the blower fan in the air passage and is formed to cover the blower fan from the another side in the axial direction, wherein the cover forms, between the cover and the inner wall, a through-passage that is configured to conduct the air blown out from the blower fan toward the another side in the axial direction; and
  • at least one swirl flow suppressor that is disposed in the through-passage and is elongated along the radial direction, wherein the at least one swirl flow suppressor is configured to suppress a swirl flow of the air generated by rotation of the blower fan, and thereby to generate an airflow that flows toward the another side in the axial direction, wherein:
  • a dimension of the at least one swirl flow suppressor, which is measured in a rotational direction of the blower fan, decreases as the at least one swirl flow suppressor extends from a radially inner side toward the radially outer side in the radial direction.

(Aspect 9)

According to aspect 9, there is provided the blower device according to any one of aspects 1 to 8, wherein:

• • a direction, which intersects both the axial direction and a rotational direction of the blower fan and is directed from another side toward one side in the rotational direction and from the other side toward the one side in the axial direction, is defined as an intersecting direction;
  • the at least one swirl flow suppressor has a one-side end surface, which faces the one side in the rotational direction, wherein the one-side end surface is formed in a curved shape that is convex in the intersecting direction toward the one side in the rotational direction; and
  • the at least one swirl flow suppressor has an another-side end surface, which faces the another side in the rotational direction, wherein the another-side end surface is formed in a curved shape that is convex in the intersecting direction toward the one side in the rotational direction.

(Aspect 10)

According to aspect 10, there is provided the blower device according to any one of aspects 1 to 9, wherein:

• • the at least one swirl flow suppressor has an end surface, which faces in the axial direction and is elongated along a rotational direction; and
  • the end surface is formed such that an acute angle, which is defined between the end surface and a virtual plane that is parallel to the rotational direction and is perpendicular to the axial direction, decreases as the end surface extends from the radially inner side toward the radially outer side.

(Aspect 11)

According to aspect 11, there is provided the blower device according to any one of aspects 1 to 10, wherein the at least one swirl flow suppressor is a plurality of swirl flow suppressors that are arranged at intervals in a circumferential direction about the axis.

(Aspect 12)

According to aspect 12, there is provided the blower device according to aspect 11, wherein the plurality of swirl flow suppressors are arranged in the circumferential direction such that the intervals include at least two different intervals which are different from each other.

(Aspect 13)

According to aspect 13, there is provided the blower device according to aspect 11, wherein the plurality of swirl flow suppressors are arranged so as to avoid overlap of respective shadows of the plurality of swirl flow suppressors that are generated when the plurality of swirl flow suppressors are optically projected from the one side in the axial direction.

(Aspect 14)

According to aspect 14, there is provided a blower device including:

• • an air conditioning case that has an inner wall, wherein the inner wall forms an air passage which is configured to conduct air;
  • a blower fan that is disposed in the air passage, wherein a direction, in which an axis of the blower fan extends, is defined as an axial direction, and the blower fan is configured to rotate toward one side in a rotational direction about the axis to draw in the air from one side in the axial direction and to blow the air out toward a radially outer side in a radial direction about the axis;
  • a cover that is disposed on another side in the axial direction with respect to the blower fan in the air passage and is formed to cover the blower fan from the another side in the axial direction, wherein the cover forms, between the cover and the inner wall, a through-passage that is configured to conduct the air blown out from the blower fan toward the another side in the axial direction; and
  • at least one swirl flow suppressor that is disposed in the through-passage and is elongated along the radial direction, wherein the at least one swirl flow suppressor is configured to suppress a swirl flow of the air generated by rotation of the blower fan, and thereby to generate an airflow that flows toward the another side in the axial direction, wherein:
  • an another-side end portion of the at least one swirl flow suppressor, which faces another side opposite to the one side in the rotational direction, is formed to extend toward the another side in the rotational direction as the another-side end portion extends from a radially inner side toward the radially outer side in the radial direction; and
  • a one-side end portion of the at least one swirl flow suppressor, which faces the one side in the axial direction, is formed to extend toward the one side in the axial direction as the one-side end portion extends from a radially inner side toward the radially outer side in the radial direction.

(Aspect 15)

According to aspect 15, there is provided a blower device including:

• • an air conditioning case that has an inner wall, wherein the inner wall forms an air passage which is configured to conduct air;
  • a blower fan that is disposed in the air passage, wherein a direction, in which an axis of the blower fan extends, is defined as an axial direction, and the blower fan is configured to rotate toward one side in a rotational direction about the axis to draw in the air from one side in the axial direction and to blow the air out toward a radially outer side in a radial direction about the axis;
  • a cover that is disposed on another side in the axial direction with respect to the blower fan in the air passage and is formed to cover the blower fan from the another side in the axial direction, wherein the cover forms, between the cover and the inner wall, a through-passage that is configured to conduct the air blown out from the blower fan toward the another side in the axial direction; and
  • at least one swirl flow suppressor that is disposed in the through-passage and is elongated along the radial direction, wherein the at least one swirl flow suppressor is configured to suppress a swirl flow of the air generated by rotation of the blower fan, and thereby to generate an airflow that flows toward the another side in the axial direction, wherein:
  • an another-side end portion of the at least one swirl flow suppressor, which faces another side opposite to the one side in the rotational direction, is formed to extend toward the one side in the rotational direction as the another-side end portion extends from a radially inner side toward the radially outer side in the radial direction; and
  • a one-side end portion of the at least one swirl flow suppressor, which faces the one side in the axial direction, is formed to extend toward the one side in the axial direction as the one-side end portion extends from a radially inner side toward the radially outer side in the radial direction.

(Aspect 16)

According to aspect 16, there is provided a blower device including:

• • an air conditioning case that has an inner wall, wherein the inner wall forms an air passage which is configured to conduct air;
  • a blower fan that is disposed in the air passage, wherein a direction, in which an axis of the blower fan extends, is defined as an axial direction, and the blower fan is configured to rotate toward one side in a rotational direction about the axis to draw in the air from one side in the axial direction and to blow the air out toward a radially outer side in a radial direction about the axis;
  • a cover that is disposed on another side in the axial direction with respect to the blower fan in the air passage and is formed to cover the blower fan from the another side in the axial direction, wherein the cover forms, between the cover and the inner wall, a through-passage that is configured to conduct the air blown out from the blower fan toward the another side in the axial direction; and
  • at least one swirl flow suppressor that is disposed in the through-passage and is elongated along the radial direction, wherein the at least one swirl flow suppressor is configured to suppress a swirl flow of the air generated by rotation of the blower fan, and thereby to generate an airflow that flows toward the another side in the axial direction, wherein:
  • an another-side end portion of the at least one swirl flow suppressor, which faces another side opposite to the one side in the rotational direction, is formed to extend toward the another side in the rotational direction as the another-side end portion extends from a radially inner side toward the radially outer side in the radial direction; and
  • a one-side end portion of the at least one swirl flow suppressor, which faces the one side in the axial direction, is formed to extend toward the another side in the axial direction as the one-side end portion extends from a radially inner side toward the radially outer side in the radial direction.

(Aspect 17)

According to aspect 17, there is provided a blower device including:

• • an air conditioning case that has an inner wall, wherein the inner wall forms an air passage which is configured to conduct air;
  • a blower fan that is disposed in the air passage, wherein a direction, in which an axis of the blower fan extends, is defined as an axial direction, and the blower fan is configured to rotate toward one side in a rotational direction about the axis to draw in the air from one side in the axial direction and to blow the air out toward a radially outer side in a radial direction about the axis;
  • a cover that is disposed on another side in the axial direction with respect to the blower fan in the air passage and is formed to cover the blower fan from the another side in the axial direction, wherein the cover forms, between the cover and the inner wall, a through-passage that is configured to conduct the air blown out from the blower fan toward the another side in the axial direction; and
  • at least one swirl flow suppressor that is disposed in the through-passage and is elongated along the radial direction, wherein the at least one swirl flow suppressor is configured to suppress a swirl flow of the air generated by rotation of the blower fan, and thereby to generate an airflow that flows toward the another side in the axial direction, wherein:
  • an another-side end portion of the at least one swirl flow suppressor, which faces another side opposite to the one side in the rotational direction, is formed to extend toward the one side in the rotational direction as the another-side end portion extends from a radially inner side toward the radially outer side in the radial direction; and
  • a one-side end portion of the at least one swirl flow suppressor, which faces the one side in the axial direction, is formed to extend toward the another side in the axial direction as the one-side end portion extends from a radially inner side toward the radially outer side in the radial direction.