WO2008068959A1

WO2008068959A1 - Air supply unit

Info

Publication number: WO2008068959A1
Application number: PCT/JP2007/070046
Authority: WO
Inventors: Masayuki Fujimoto; Toshikatsu Mori; Toshiaki Tsutsumi
Original assignee: Valeo Thermal Systems Japan Corporation
Priority date: 2006-12-05
Filing date: 2007-10-15
Publication date: 2008-06-12
Also published as: JP2008138643A; JP5163974B2

Abstract

Air supply capacity, silent properties, and the like, can be sustained at higher levels as compared with the prior art when a reduced scroll chamber is designed. In an air supply unit designed such that the dimensions of a spiral scroll chamber (20) letting air flow generated by a fan (4) pass are enlarged in the radial and axial directions, enlargement ratio of cross-sectional area of the scroll chamber (20) varies to become larger in the range of first winding angle ϑ or above than the enlargement ratio in the range smaller than the first winding angle ϑ, and the axial dimension of the scroll chamber (20) is enlarged in the range of first winding angle ϑ or above.

Description

Specification

Blower unit

Technical field

TECHNICAL FIELD [0001] The present invention relates to a blower unit used for a vehicle air conditioner and the like, and more particularly to reduction of a scroll chamber.

Background art

[0002] In designing a vehicle air conditioner, downsizing the HVAC unit is a constantly required issue. One of the ways to reduce the size of the HVAC unit is to reduce the scroll chamber in which the blower is installed. It is possible. When reducing the size of the scroll chamber, 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 air passage shape that can reduce the scroll chamber without impairing the air blowing capacity and quietness.

[0003] In order to deal 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 discharge port of the casing, so that the size in the axial direction is increased (rate ) Is changed so that the amount of expansion (rate) of the cross-sectional area of the scroll chamber becomes substantially constant with respect to the scroll winding angle (see Patent Document 1). As a result, it is said that the size of the scroll chamber in the radial direction can be reduced while maintaining the air feeding efficiency and quietness.

Patent Document 1: JP 2002-202098

Disclosure of the invention

Problems to be solved by the invention

[0004] 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 wrap angle (Patent Document 1, Paragraph 0036). (See Figure 4, “Line α”). In addition, the expansion of the scroll chamber in the axial direction starts immediately after the scroll starts to roll (near the tongue) (see the same document, paragraph 0027, Fig. 3, "Line X").

[0005] However, according to the above-mentioned conventional invention! In addition to being substantially constant in the angular range, the axial dimension of the scroll chamber starts to increase immediately from the vicinity of the tongue. Because of its easy structure, there was room for improvement in terms of air blowing capacity (efficiency) and quietness.

[0006] Therefore, an object of the present invention is to maintain a blowing capacity (efficiency), quietness, etc. at a higher level than before in designing a reduced scroll chamber.

Means for solving the problem

[0007] The present invention for solving the above problems is a blower unit that is designed so that the size of a scroll chamber having a spiral shape and through which an air flow generated by a blower flows is expanded in a radial direction and an axial direction. The scroll chamber's cross-sectional area enlargement ratio power changes in a range greater than or equal to the first winding angle to be larger than the enlargement ratio in a range smaller than the first winding angle, and the scroll chamber's axial dimensional force It expands in the range beyond the first winding angle (Claim 1).

[0008] As described above, in the present invention, the enlargement ratio of the cross-sectional area of the scroll chamber changes greatly starting from the first winding angle. Further, in the present invention, the size of the scroll chamber in the axial direction 1S expands in the range equal to or larger than the first winding angle, and does not expand in the range smaller than the first winding angle. That is, up to the first winding angle of the scroll starting force and the first winding angle, the cross-sectional area of the scroll chamber is enlarged only in the radial direction. As a result, the internal air flow in which the cross-sectional area of the scroll chamber does not rapidly increase from the beginning of winding is more stable than in the conventional structure. Therefore, when designing a reduced scroll chamber, the blowing capacity (efficiency), quietness It becomes possible to maintain the property etc. at a higher level than before.

[0009] Further, according to the present invention, the shape of the scroll chamber having a spiral shape and through which the air flow generated by the blower circulates is a characteristic line (D ), The characteristic line (D) has the same expansion ratio as the reference line (A) set based on the predetermined blower diameter and the first divergence angle. Line (C) and a reduced line (B) set based on a predetermined blower diameter and a second spread angle smaller than the first spread angle, and the scroll chamber winding angle is In a range smaller than the first winding angle, it overlaps with the reduction line (B), and the scroll chamber is wound. The corner overlaps the quasi-reference line (c) in the range of the first winding angle or more, and the axial dimensional force of the scroll chamber expands in the range of the first winding angle or more. (Claim 2).

[0010] 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 reduced line is indicated as B. The quasi-reference line C is obtained by translating the reference line A so that it intersects the reduction line B at the first winding angle Θ. The characteristic line D used for the design of the scroll shape overlaps with the reduction line B in the range where the winding angle is smaller than Θ, and overlaps with the quasi-reference line C in the range beyond Θ. As a result, the shape of the scroll chamber is designed based on the enlargement ratio of the reduction line B set with a small divergence angle in the range where the winding angle is smaller than Θ, and in the range where the winding angle is more than Θ, It is designed based on the magnification of reference line A set with a large divergence angle. In other words, the magnification ratio power of the cross-sectional area of the scroll chamber greatly changes at the first winding angle Θ. Further, similarly to the configuration of claim 1, the axial dimension of the scroll chamber is not expanded to the first winding angle Θ. As a result, the internal air flow that the cross-sectional area of the scroll chamber does not rapidly increase from the beginning of winding is more stable than the conventional structure. Therefore, in designing a reduced scroll chamber, the blowing capacity (efficiency), It is possible to maintain quietness 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 the reduction line, the optimum scroll shape at each blower diameter and divergence angle can be obtained by calculation, reducing man-hours, etc. Is possible.

Further, as a result of an investigation by the present inventor, it has been found that the first winding angle in the configuration according to claim 1 or 2 is preferably 150 ° to 170 ° (claim). 3)

Yes

The invention's effect

As described above, according to the present invention, the enlargement ratio of the cross-sectional area of the scroll chamber varies greatly at the first winding angle (150 ° to 170 °), and the axial dimension of the scroll chamber Is expanded only in the range of the first winding angle or more, so that the internal air flow that the cross-sectional area of the scroll chamber does not rapidly expand from the start of winding is more stable than the conventional structure. In designing a scroll room with a reduced size, follow the ventilation capacity (efficiency), quietness, etc. It becomes possible to maintain at a higher level than ever. When designing the scroll shape based on the characteristic line, the blower diameter and divergence angle of the reference line (quasi-reference line) and the reduction line are selected as appropriate so The optimal scroll shape can be calculated, and man-hours can be reduced.

Brief Description of Drawings

FIG. 1 is a cross-sectional view showing a structure of a blower unit according to the present embodiment.

FIG. 2 is a view showing the features of the scroll chamber according to the present embodiment, where (a) is a plan view and (b) is a front view.

[Fig. 3] (a) is a graph showing the relationship between the winding angle and the cross-sectional area of the air passage, with respect to the reference line, reduction line, and quasi-reference line, and (b) is the air angle and cross-sectional area of the air passage. Is a graph showing the relationship between the reference line, the reduction line, the quasi-reference line, and the characteristic line.

FIG. 4 is a graph showing the relationship between the axial dimension and the winding angle of the scroll chamber (air passage) according to this example.

FIG. 5 is a graph showing the relationship between the air flow rate, the total pressure, the blower speed, the sound pressure, and the current used in the scroll chamber according to the present embodiment.

Explanation of symbols

[0014] 1 Blower unit

2 Casing

3 Motor

4 Blower

12 Air duct

13 Suction port

14 Discharge port

19 Tongue

20 Scroll room

A Reference line

B reduction line

C quasi-reference line D Characteristic line

Dl radial dimension

D2 Axial dimension

BEST MODE FOR CARRYING OUT THE INVENTION

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

Example 1

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 the motor 3, blower 4, and other necessary mechanisms therein. The casing 2 generally consists of two parts 2a and 2b, and is configured to sandwich the mechanism from above and below in the figure. The casing 2 includes a motor installation unit 10 where the motor 3 is installed, a blower installation unit 11 where the blower 4 is installed, an air flow path 12 serving as an air flow path through the blower 4, and an upper part of the blower 4 (the motor installation unit Open to the center of the blower 4 at a position opposite to the blower 10) and open to the suction port 13 communicating with one end of the air supply path 12 through the blower installation part 11 and to the other end of the air supply path 12. A discharge port 14 is formed. A scroll chamber 20 is configured by the blower installation part 11 and the air passage 12.

[0018] The motor 3 is a drive source for rotating the blower 4, and includes a main body portion 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 portion 25 to the outside. It is configured with The main body 25 is fixed to the motor installation part 10 formed in the casing 2, and the blower 4 is fixed to the drive shaft 26. In this embodiment, screw grooves are formed in the drive shaft 26. The motor 3 is driven by a current from a vehicle-mounted battery, and is controlled by a control signal from a predetermined control unit.

The blower 4 generates an air flow by rotating with the driving force of the motor 3. The blower 4 faces the motor 3 and has a bottom face 30 having a substantially triangular pyramid shape, a plurality of wing parts 31 erected along the outer edge of the bottom face part 30, and the suction port 13 and the upper end of each wing part 32. It has a ring-shaped upper surface portion 32 to be connected. A boss portion 35 in which a screw groove is formed 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 motor 3 After screwing the screw groove of the drive shaft 26, the end of the drive shaft 26 protruding from the boss portion 25 is tightened by the bolt 36 to fix the motor 3 and the blower 4. Since the upper surface portion 32 has a ring shape, the central portion thereof is an opening 40, so that air from the suction port 13 is taken into the central portion of the blower 4. Each wing part 31 is installed at an 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.

[0020] FIGS. 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 portion 19 toward the outlet 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 of the air passage 12 (see FIG. 2 (a)) 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. 2 (b)) extends from the first winding angle Θ to the discharge port 13 and is constant in the range of winding angles 0 ° to Θ. The preferred range of the first winding angle Θ is 150 ° to 170.

FIG. 3 (a) shows a graph showing the relationship between the winding angle of the air passage and the cross-sectional area.

Solid line A is data in the case where the scroll shape of the air passage 12 is a blower diameter of 140 mm and a spread angle of 4.5 °, and this is referred to as a reference line. The broken line B is the data when the blower diameter is 140 mm and the spread angle is 2.8 °, and this is called the reduction line. The scroll shape related to the reference line A is said 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 140mm and a wide S angle of 2.8 ° related to the reduction line B is an example of a design that can be made to meet the restrictions on in-vehicle space. The alternate long and short dash 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 called a quasi-reference line.

[0023] The scroll chamber 20 according to the present embodiment is designed according to a characteristic line indicated by a thick line D in Fig. 3 (b). The characteristic line D has the same characteristics as the contraction line B in the range up to the winding angle 0 ° force Θ, and the same characteristics as the quasi-reference line C in the range beyond the winding angle Θ. It is what has. That is, in the scroll chamber 20 according to the present invention, the enlargement ratio of the cross-sectional area greatly changes at the winding angle Θ.

[0024] Furthermore, the axial dimension D2 of the air passage 12 is constant in the range from the winding angle 0 ° to Θ, as shown by the solid line E in Fig. 4, and in the range above the winding angle Θ. (The dashed-dotted line 9 in FIG. 1 is not enlarged in the axial direction! / Is a virtual line indicating the discharge port in the case). That is, the expansion of the air passage 12 in this configuration is performed only by increasing the radial dimension D1 in the range up to the winding angle 0 ° force, and Θ, and in the range beyond the winding angle Θ, the radial direction is increased. This is done by expanding both the dimension D1 and the axial dimension D2.

[0025] By adopting such a design, the entire scroll chamber 20 can be reduced in the radial direction rather than the reference scroll shape (blower diameter 140mm, spread angle 4.5 · 5 °) indicated by the reference line A above. Since the cross-sectional area (total volume) of the air passage 12 can be made larger than the scroll shape (blower diameter 140mm, spread angle 2.8 °) shown by the reduction line B, the air blowing capacity or efficiency can be reduced. Can be kept high. In addition, since the expansion of the dimension D2 in the axial direction does not start until the winding angle Θ, turbulent flow and noise are generated that do not cause the cross-sectional area of the air passage 12 to rapidly increase from the vicinity of the tongue portion 19 as in the conventional structure. It has a structure that is difficult to do.

[0026] Table 1 below shows a scroll chamber 20 having the shape of the characteristic line D according to the present embodiment (this configuration) and a scroll chamber having the shape of the reduction line B (blower diameter 140 mm, spread angle 2). It is a performance comparison with 8 °). 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 (480m ³ / h), and when using low speed ( Even at 330 m ³ / h), significant improvements are seen in noise and specific noise.

[0027] [Table 1]

[0028] FIG. 5 shows the relationship between the amount of air blown in the blower unit 1 according to this embodiment and the total pressure, blower rotational speed, or sound pressure. As shown in the figure, the sound pressure is kept almost constant even when the air flow increases. From this, the blower unit 1 according to the present embodiment is It turns out that it has sufficient silence.

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

Claims

The scope of the claims

[1] In a blower unit that has a spiral shape and is designed so that the dimensions of the scroll chamber in which the airflow generated by the blower flows is expanded in the radial direction and the axial direction.

The expansion ratio power s of the cross-sectional area of the scroll chamber changes so as to be larger than the expansion ratio in a range smaller than the first winding angle in a range greater than or equal to the first winding angle, and in the axial direction of the scroll chamber. Dimensional force Expanding in a range equal to or greater than the first winding angle.

[2] In the air blowing unit, 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 indicating the relationship between the cross-sectional area of the scroll chamber and the winding angle.

The characteristic line is based on a predetermined blower diameter and a first divergence angle! /, A quasi-reference line having the same magnification as the reference line set, and a predetermined blower diameter and the first divergence angle. Smaller! /, Based on the second divergence angle! /, And based on the set reduction line! /, And the scroll chamber winding angle is greater than the first winding angle. The scroll line overlaps with the reduced line in a small range, and the wrapping angle of the scroll chamber overlaps with the quasi-reference line in a range of the first winding angle or more,

Dimensional force in the axial direction of the scroll chamber The blower unit expands in a range equal to or greater than the first winding angle.

[3] The blower unit according to claim 1 or 2, wherein the first winding angle is 150 ° to 170 °.