JP5163974B2 - Blower unit - Google Patents

Description

  The present invention relates to a blower unit used in a vehicle air conditioner and the like, and more particularly to reduction of a scroll chamber.

  In the design of a vehicle air conditioner, downsizing of the HVAC unit is always a challenge, but as one method for reducing the size of the HVAC unit, it is possible to reduce the scroll chamber in which the blower is installed. Conceivable. When the scroll chamber is reduced, there are problems such as a reduction in blowing capacity and noise due to turbulence caused by changing the optimum shape of the blowing path. Therefore, it is important to design an airflow path shape that can reduce the scroll chamber without impairing the air blowing capacity and silence.

In order to cope with the above problems, the scroll chamber is configured to expand not only in the radial direction but also in the axial direction toward the blower outlet of the casing, and the expansion width (rate) of the dimension in the axial direction is changed. An invention is disclosed in which the amount of expansion (rate) of the cross-sectional area of the scroll chamber is substantially constant with respect to the scroll winding angle (see Patent Document 1). Thereby, it is supposed that the size of the scroll chamber in the radial direction can be reduced while maintaining the blowing efficiency and the silence.
JP 2002-202098 A

  In the invention disclosed in Patent Document 1 above, the enlargement ratio of the cross-sectional area of the scroll chamber is made substantially constant with respect to the winding angle (refer to Document 1, Paragraph 0036, FIG. 4, “Folded Line α”). ). In addition, the expansion of the scroll chamber in the axial direction starts immediately after the scroll starts to be wound (near the tongue) (see the same document, paragraph 0027, FIG. 3, “polyline X”).

  However, in the above-described conventional invention, the expansion ratio of the cross-sectional area of the scroll chamber is substantially constant over the entire winding angle range, and the expansion of the dimension in the axial direction of the scroll chamber is started immediately from the vicinity of the tongue, thereby Since the cross-sectional area of the chamber suddenly expanded from the beginning of the winding and turbulence was likely to occur, there was room for improvement in terms of blowing capacity (efficiency) and quietness.

  SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to maintain a blowing capacity (efficiency), quietness, etc. at a higher level than before when designing a reduced scroll chamber.

In the present invention, the shape of the scroll chamber having a spiral shape and through which the air flow generated by the blower flows is designed based on the characteristic line (D) indicating the relationship between the cross-sectional area of the scroll chamber and the winding angle. In the blower unit, the characteristic line (D) includes a quasi-reference line (C) having the same enlargement ratio as a reference line (A) set based on a predetermined blower diameter and a first spread angle, A reduction line (B) set based on a blower diameter and a second spread angle smaller than the first spread angle, and a winding angle of the scroll chamber is smaller than the first winding angle. The scroll chamber overlaps with the reduction line (B), the scroll chamber overlaps with the quasi-reference line (C) in a range equal to or greater than the first winding angle, and the axial dimension of the scroll chamber is In the range of more than 1 winding angle Is characterized in that the expanding Te (claim 1).

In FIG. 3, the characteristic line is indicated as D, the reference line is indicated as A, the quasi-reference line is indicated as C, and the reduction line is indicated as B. The quasi-reference line C is obtained by translating the reference line A so as to intersect the reduction line B at the first winding angle θ. The characteristic line D used for designing the scroll shape overlaps the reduction line B in a range where the winding angle is smaller than θ, and overlaps the quasi-reference line C in a range equal to or larger than θ. Thereby, the shape of the scroll chamber is designed based on the enlargement ratio of the reduction line B set with a small spread angle when the winding angle is smaller than θ, and large when the winding angle is larger than θ. It is designed based on the enlargement ratio of the reference line A set with a corner. That is, the expansion ratio of the cross-sectional area of the scroll chamber changes greatly at the first winding angle θ. For this reason , the dimension of the scroll chamber in the axial direction is not increased to the first winding angle θ.

  As a result, the cross-sectional area of the scroll chamber does not increase suddenly from the beginning of winding, and the internal air flow is more stable than the conventional structure, so in designing a reduced scroll chamber, the blowing capacity (efficiency), It becomes possible to maintain silence etc. at a higher level than before. In addition, by appropriately selecting the blower diameter and divergence angle of the reference line (quasi-reference line) and reduction line, the optimum scroll shape for each blower diameter and divergence angle can be calculated, reducing man-hours, etc. Is possible.

Further, as a result of investigation by the present inventor, it has been found that the first winding angle in the configuration according to claim 1 is preferably 150 ° to 170 ° (claim 2 ).

As described above, according to the present invention, when the scroll shape is designed based on the characteristic line, each blower diameter can be selected by appropriately selecting the blower diameter and the spread angle of the reference line , the quasi-reference line, and the reduction line. In addition, an optimal scroll shape at the spread angle can be obtained by calculation, and man-hours can be reduced. Even in such a scroll shape calculated from the calculation, the enlargement ratio of the cross-sectional area of the scroll chamber is greatly changed at the first winding angle (150 ° to 170 °), and the axial dimension of the scroll chamber is Since the cross-sectional area of the scroll chamber does not suddenly increase from the beginning of winding and the internal air flow is more stable than that of the conventional structure, it is reduced by adopting a configuration that expands only in the range of the first winding angle or more. In designing the scroll chamber, the air blowing capacity (efficiency), quietness, and the like can be maintained at a higher level than before.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

  FIG. 1 shows a blower unit 1 that constitutes a part of the HVAC unit. The blower unit 1 includes a casing 2, a motor 3, and a blower 4.

  The casing 2 is made of a material such as resin, and houses a motor 3, a blower 4, and other necessary mechanisms therein. The casing 2 is generally composed of two parts 2a and 2b, and is configured to sandwich the mechanism from above and below in the drawing. The casing 2 includes a motor installation unit 10 in which the motor 3 is installed, a blower installation unit 11 in which the blower 4 is installed, a blower path 12 serving as an air flow path by the blower 4, and an upper part of the blower 4 (in the motor installation unit 10 A suction port 13 that opens toward the center of the blower 4 and communicates with one end of the air passage 12 through the blower installation portion 11 and a discharge port 14 that opens at the other end of the air passage 12. Is formed. A scroll chamber 20 is configured by the blower installation portion 11 and the air passage 12.

  The motor 3 is a drive source for rotating the blower 4, and includes a main body 25 that houses an electromagnet, a rotor, and the like, and a drive shaft 26 that transmits a driving force generated in the main body 25 to the outside. Composed. The main body portion 25 is fixed to the motor installation portion 10 formed in the casing 2, and the blower 4 is fixed to the drive shaft 26. In this embodiment, a screw groove is formed in the drive shaft 26. The motor 3 is driven by a current from a vehicle battery and is controlled by a control signal from a predetermined control unit.

  The blower 4 generates an air flow by rotating by the driving force of the motor 3. The blower 4 faces the motor 3 and has a substantially triangular pyramid-shaped lower surface portion 30, a plurality of wing portions 31 erected along the outer edge of the lower surface portion 30, faces the suction port 13, and is connected to the upper end of each wing portion 32. The ring-shaped upper surface portion 32 is configured. A boss portion 35 formed with a screw groove is formed at the top of the triangular pyramid shape of the lower surface portion 30, and the screw groove of the boss portion 35 and the screw groove of the drive shaft 26 of the motor 3 are screwed together. Thereafter, the motor 3 and the blower 4 are fixed by fastening the end portion of the drive shaft 26 protruding from the boss portion 25 with a bolt 36. Since the upper surface portion 32 has a ring shape, the central portion thereof is an opening 40, and air from the suction port 13 is taken into the central portion of the blower 4. Each wing portion 31 is installed at a predetermined angle with respect to the radial direction of the blower 4. With the above configuration, when the blower 4 rotates, an air flow is generated substantially radially from the center of the blower 4.

  2 to 4 show the shape characteristics of the scroll chamber 20 of the blower unit 1 according to the present invention. The cross-sectional area of the air passage 12 constituting the scroll chamber 20 is designed to gradually increase from the tongue 19 toward the discharge port 13.

  In the configuration according to the present embodiment, the enlargement ratio of the cross-sectional area of the air passage 12 with respect to the winding angle changes so as to increase from a first winding angle θ described later. Further, in the configuration according to the present embodiment, the radial dimension D1 (see FIG. 2A) of the air passage 12 is expanded from the tongue portion 19 to the discharge port 13 as in the prior art, and the shaft The direction dimension D2 (see FIG. 2B) extends to the discharge port 13 starting from the first winding angle θ, and is constant in the range of the winding angle 0 ° to θ. A preferable range of the first winding angle θ is 150 ° to 170 °.

  FIG. 3A shows a graph showing the relationship between the winding angle of the air passage and the cross-sectional area. A solid line A is data when the scroll shape of the air passage 12 is a blower diameter of 140 mm and a spread angle of 4.5 °, which is referred to as a reference line. A broken line B is data when the blower diameter is 140 mm and the spread angle is 2.8 °, and this is referred to as a reduction line. The scroll shape according to the reference line A is considered to be excellent in terms of air blowing capacity, quietness, and the like, and is an example of a design that is generally used when there is no particular restriction on the in-vehicle space. The scroll shape with a blower diameter of 140 mm and a spread angle of 2.8 ° according to the reduction line B is an example of a design made to cope with restrictions on the in-vehicle space. A one-dot chain line C is obtained by translating the reference line A so that the reference line A and the reduction line B intersect at the position of the winding angle θ, and is referred to as a quasi-reference line.

  And the scroll chamber 20 which concerns on a present Example is designed according to the characteristic line shown by the thick line D in FIG.3 (b). The characteristic line D has the same characteristics as the contraction line B in the range from 0 ° to θ of the winding angle, and has the same characteristics as the quasi-reference line C in the range of the winding angle θ or more. . That is, the expansion ratio of the cross-sectional area of the scroll chamber 20 according to the present invention greatly changes at the winding angle θ.

  Furthermore, as shown by the solid line E in FIG. 4, the dimension D2 in the axial direction of the air passage 12 is constant in the range of the winding angle from 0 ° to θ, and is expanded in the range of the winding angle θ or more. (The dashed-dotted line 9 in FIG. 1 is a virtual line which shows the discharge outlet when not expanding to an axial direction.). That is, the expansion of the air passage 12 in this configuration is performed only by increasing the radial dimension D1 in the range from the winding angle 0 ° to θ, and in the range above the winding angle θ, the radial dimension D1 and This is done by expanding both axial dimensions D2.

  By adopting such a design, the entire scroll chamber 20 can be reduced in the radial direction as compared to the reference scroll shape (blower diameter 140 mm, spread angle 4.5 °) indicated by the reference line A. Since the cross-sectional area (total volume) of the air passage 12 can be made larger than the scroll shape (blower diameter 140 mm, spread angle 2.8 °) indicated by the reduction line B, the air blowing capacity or efficiency is maintained high. be able to. Further, since the expansion of the dimension D2 in the axial direction does not start until the winding angle θ, the cross-sectional area of the air passage 12 does not increase suddenly from the vicinity of the tongue portion 19 unlike the conventional structure, and turbulence and noise are generated. The structure is difficult to do.

  Table 1 below shows a scroll chamber 20 (this configuration) having the shape of the characteristic line D according to this embodiment, and a scroll chamber having the shape of the reduction line B (blower diameter 140 mm, spread angle 2.8 °). ) And performance comparison. As shown in this table, this configuration exceeds all of the total pressure, power consumption, total efficiency, noise, and specific noise when using high speed (480m3 / h), and when using low speed (330m3). / H), there is a significant improvement in noise and specific noise.

  Moreover, in FIG. 5, the relationship between the ventilation volume in the ventilation unit 1 which concerns on a present Example, and a total pressure or a blower rotational speed or a sound pressure is shown. As shown in the figure, the sound pressure is kept substantially constant even when the amount of blown air increases. From this, it turns out that the ventilation unit 1 which concerns on a present Example has sufficient silence.

  In the above embodiment, the blower diameter of the reference line A (quasi-reference line C) is 140 mm, the spread angle is 4.5 °, the blower diameter of the reduction line B is 140 mm, and the spread angle is 2.8 °. However, the present invention is not limited to this, and the blower diameter and divergence angle of each line can be appropriately selected.

It is sectional drawing which shows the structure of the ventilation unit which concerns on a present Example. It is a figure which shows the characteristic of the scroll chamber which concerns on a present Example, (a) is a top view, (b) is a front view. (A) is a graph showing the relationship between the winding angle of the air passage and the cross-sectional area, with respect to the reference line, the reduction line, and the quasi-reference line, (b) is the relationship between the winding angle of the air passage and the cross-sectional area, It is a graph shown about a reference line, a reduction line, a semi-reference line, and a characteristic line. It is a graph which shows the relationship between the dimension of the axial direction of the scroll chamber (air flow path) which concerns on a present Example, and a winding angle. It is a graph which shows the relationship between the ventilation volume in the scroll chamber which concerns on a present Example, a total pressure, a blower speed, a sound pressure, and an operating current.

1 Blower unit 2 Casing 3 Motor 4 Blower 12 Blower passage 13 Suction port 14 Discharge port 19 Tongue portion 20 Scroll chamber A Reference line B Reduction line C Quasi-reference line D Characteristic line D1 Radial dimension D2 Axial dimension

Claims (2)

In the blower unit, the shape of the scroll chamber in which the air flow generated by the blower having a spiral shape circulates is designed based on the characteristic line indicating the relationship between the cross-sectional area of the scroll chamber and the winding angle.
The characteristic line includes a quasi-reference line having the same enlargement ratio as a reference line set based on a predetermined blower diameter and a first spread angle, and a second smaller than the predetermined blower diameter and the first spread angle. And the scroll chamber winding angle overlaps with the reduction line in a range smaller than the first winding angle, and the scroll chamber winding angle is set to the first reduction angle. Overlaps the quasi-reference line in a range of one or more winding angles,
The blower unit characterized in that the dimension in the axial direction of the scroll chamber expands in a range equal to or larger than the first winding angle. It said first winding angle, blower unit according to claim 1, wherein it is 0.99 ° to 170 °.

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