JPH07119686A - Swirl blower - Google Patents

Abstract

PURPOSE:To decrease manufacturing by comparatively simplifying the form of a blade, and to improve aerodynamic characteristics so as to obtain high efficiency. CONSTITUTION:A rotating impeller 2 is stored in a circular casing 1 having an annular passage 1a formed on the outer peripheral part, and many blades 21 formed at equal spaces in the peripheral direction on the outer peripheral part are located in the annular passage 1a. Air is sucked in a vortex chamber 2a formed between the blades 21 through an inlet 11, and the air swirled and compressed in the vortex chamber 2a is discharged to a discharge port 12. The respective blades 21 are formed by a plate piece projected rectilinearly from the blade surface of the impeller 2, the inner ends and outer ends of the respective blades 21 are respectively formed in such a manner as to make designated angles alpha, beta to a line L extended from the center of rotation of the impeller 2 in the opposite direction to the rotating direction of the impeller, and the whole of the blade is recessed in the rotating direction of the impeller.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a swirl blower, and more particularly to a swirl blower which can be preferably used as a secondary air supply source for a vehicle running engine.

[0002]

2. Description of the Related Art A vortex flow blower is one in which a rotating impeller is provided in a circular casing having an annular flow path, and gas is sucked into a vortex chamber formed between the vanes, swirl-compressed and discharged. Since it is small and can obtain high discharge pressure,
Widely used as an air source for machinery.

An example thereof will be explained with reference to FIGS. 9 and 10. A circular disk-shaped impeller 2 is provided in a circular casing 1 with its center fixed to a rotating shaft 3, and the casing 1 has an outer peripheral portion. The entire circumference has a semicircular cross section and bulges forward to form an annular flow path 1a inside. The casing 1 is provided with a suction port 11 and a discharge port 12 adjacent to each other at one location in the circumferential direction, and opens into the annular flow channel 1a.

The outer peripheral portion of the impeller 2 forms a curved surface continuous with the inner surface of the bulging portion of the casing 1 to form the annular flow passage 1a having a substantially circular cross section (FIG. 10). A large number of plate-shaped blades 21 are formed in a radial straight line at equal intervals in the direction. These blades 21 form a quarter circle and project into the latter half of the annular flow path 1a.

When the impeller 2 rotates (arrow in FIG. 9), gas (air) is sucked from the suction port 11 into the vortex chamber 2a formed between the blades 21, and the gas is swirled as the impeller 2 rotates. Room 2
It is orbitally compressed in a and discharged from the discharge port 12.

Various attempts have been made to improve the aerodynamic characteristics of such a vortex flow blower to further improve the efficiency. For example, in Japanese Patent Laid-Open No. 3-175196, the impeller blades have a complicated three-dimensional shape. Is shown (first conventional example). In Japanese Utility Model Publication No. 55-48158, a plate-shaped blade provided on the plate surface of an impeller is shown to be curved in a slightly convex shape in the rotational direction (second conventional example).

[0007]

However, the blower of the first conventional example has a problem that it requires a great deal of labor and cost to manufacture because the shape of the blade is complicated. Further, in the second conventional example, the blade shape is not along the swirl flow in the vortex chamber, so that the improvement of the aerodynamic characteristics is not yet sufficient.

The present invention solves the above problems, and an object thereof is to provide a swirl blower in which the shape of the blade is relatively simple, the labor for manufacturing is reduced, and the aerodynamic characteristics are also improved to obtain high efficiency. To do.

[0009]

The structure of the present invention will be described. A circular casing 1 having an annular flow passage 1a formed in the outer peripheral portion thereof.
A rotating impeller 2 is housed therein, and a large number of blades 21 are formed in the outer peripheral portion of the impeller 2 at equal intervals in the circumferential direction in the annular flow passage 1a. In the vortex flow blower that sucks the gas into the vortex chamber 2a from the suction port 11 opening to the annular flow passage 1a, and discharges the gas swirled and compressed in the vortex chamber 2a to the discharge port 12 opening to the annular flow passage 1a, Each of the blades 21 is configured by a plate body that linearly projects from the plate surface of the impeller 2, and each blade 2
The inner end and the outer end of 1 are respectively formed so as to form predetermined angles α and β in a direction opposite to the impeller rotation direction with respect to a line L extending from the rotation center of the impeller 2, and the entire impeller is rotated. It is concave in the direction.

[0010]

In the above structure, the gas sucked into the swirl chamber 2a from the suction port 11 becomes a swirl flow here, but the swirl chamber 2a
The blade 21 forming a has an inner end and an outer end that form predetermined angles α and β, respectively, and has a concave shape in the impeller rotation direction, so that swirling of the gas in the vortex chamber 2a is not hindered and inflow loss is reduced. And turbulent flow loss are reduced and aerodynamic characteristics are improved.

[0011]

Embodiment 1 In FIGS. 1 and 2, a circular casing 1 in which an impeller 2 whose details will be described later is installed is a container-like rear portion 13 having a U-shaped cross section, and a curved surface continuous so as to cover its opening. And a front surface portion 14 forming the. That is,
The outer peripheral portion of the casing front surface portion 14 has a semicircular cross section and bulges forward, and the inner peripheral portion has a gentle chevron cross section with the center at the apex.

The center of the impeller 2 housed in the casing 1 is fixed to the tip of a rotary shaft 3 which penetrates the center of the rear surface of the casing 1 and rotates in the direction shown by the arrow in FIG. The impeller 2 has front and rear surfaces (left and right in FIG. 2) of a thick outer peripheral portion.
Is close to the inner walls of the back surface part 13 and the front surface part 14 of the casing 1, and the outer peripheral surface of the impeller 2 is located between the inner wall of the casing 1 and the inner wall of the front surface part 14.
It has a curved cross section that is continuous with the inner wall surface of the outer peripheral portion. Thus, an annular flow passage 1a having a closed cross section is formed along the entire circumference of the outer peripheral portion of the casing 1, and the annular flow passage 1a has a semicircular cross sectional space inside the casing front surface portion 14 and a substantially semicircular cross sectional space inside the casing back surface portion 13. Has become.

A large number of blades 21 are formed on the outer peripheral surface of the impeller 2 at equal intervals in the circumferential direction.
Protrudes into the substantially quarter-circular cross-section space of the annular flow path 1a.
That is, each blade 21 rises linearly from the outer peripheral surface of the impeller 2 having a curved cross section and forms a constant gap between the blade 21 and the outer peripheral wall of the casing 1 to form a substantially quarter-circular cross sectional space of the annular flow path 1a. is occupying.

Each of the blades 21 is curved in an arc shape as shown in FIG. 1 in a plan view, and the tangent line between the inner end and the outer end of the blade 21 is in the impeller rotation direction with respect to the line L extending from the rotation center of the impeller 2. And a predetermined angle α, β in the opposite direction. Hereinafter, α is referred to as a circumferential inlet angle, and β is referred to as a circumferential outlet angle.

A suction port 11 and a discharge port 12 are provided at one location on the outer peripheral wall of the casing 1 so as to be partitioned by a partition wall adjacent to the outer end of the impeller 2. Inside the vortex chamber 2a formed between the blades 21 of the
Air is sucked from 1. The sucked air generates a swirling flow in accordance with the rotational movement of the vortex chamber 2a, is compressed and pressurized, and is discharged from the discharge port 12.

In the process of generating a swirling flow in the vortex chamber 2a, the blade 21 has a predetermined inlet angle α and outlet angle β in the circumferential direction as described above, and the blade 21 as a whole is in the rotating direction of the impeller 2. Since the concave arc surface is formed, the inflow loss and turbulent flow loss of the swirling flow are sufficiently reduced, and the aerodynamic characteristics are improved.

This effect is shown in FIG. 3, where the circumferential inlet angle α
The efficiency of the blower of the present invention in which the inlet angle α and the outlet angle β are given a predetermined angle is improved as compared with the conventional blower in which the outlet angle β is 0 °. Particularly, when the inlet angle α = 35 ° and the outlet angle β = 30 °, the efficiency shows the maximum value, and the efficiency is improved by about 2% as compared with the conventional blower. To support this, as shown in FIG. 4, α = 35 °, β = 3
It is known that the blower of the present invention having 0 ° has the correlation curve of the flow coefficient and the pressure coefficient above the one of the conventional blower, and the aerodynamic characteristics are improved.

[0018]

Second Embodiment In FIGS. 5 and 6, the suction port 11 and the discharge port 12 are provided on the front surface portion 14 of the casing 1 and open to the annular flow passage 1a. Each blade 21 on the impeller 2 is the same as the first embodiment in plan view, but is different in side view. That is, as shown in FIG. 6, in the outer peripheral portion of the impeller 2, a concave groove having a semicircular cross section is formed continuously with the inner wall of the outer peripheral portion of the front surface of the casing 1 which has a semicircular cross section and bulges forward.
An annular channel 1a having a circular cross section which is closed as a whole is formed. Then, a blade 21 having a semicircular shape is linearly projected from the concave groove in the annular channel 1a.

Thus, by making the blades 21 semicircular, as shown in FIG. 7, the efficiency is higher in the region where the flow coefficient is particularly larger than that of the conventional blower. Also, FIG.
As is known in the art, the correlation curve between the flow coefficient and the pressure coefficient is also above the conventional blower, and the aerodynamic characteristics are improved.

[0020]

As described above, the vortex flow blower of the present invention has improved the aerodynamic characteristics of the blower and has a high efficiency without the complicated three-dimensional shape of the blade, with a simple and inexpensive structure. is there.

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view of a vortex flow blower according to an embodiment of the present invention, which is a cross-sectional view taken along line I-I of FIG.

2 is a cross-sectional view of the vortex blower, which is a cross-sectional view taken along line II-II of FIG.

FIG. 3 is a diagram showing an efficiency improvement region when a circumferential inlet angle and an outlet angle of a blade are changed.

FIG. 4 is a diagram comparing a correlation curve of a flow coefficient and a pressure coefficient with a conventional product.

5 is a vertical cross-sectional view of a swirl blower according to another embodiment of the present invention, which is a cross-sectional view taken along the line VV of FIG.

6 is a transverse cross-sectional view of the vortex flow blower, which is a cross-sectional view taken along line VI-VI of FIG.

FIG. 7 is a graph comparing blower efficiency with a conventional product.

FIG. 8 is a diagram comparing a correlation curve between a flow coefficient and a pressure coefficient with a conventional product.

FIG. 9 is a vertical cross-sectional view of a swirl blower in a conventional example.
It is a sectional view taken along line IX-IX of No. 0.

FIG. 10 is a cross-sectional view of a vortex flow blower in a conventional example, which is a cross-sectional view taken along line XX of FIG.

[Explanation of symbols]

 1 Casing 1a Annular flow path 11 Suction port 12 Discharge port 2 Impeller 2a Vortex chamber 21 Blade

Claims (1)

[Claims] 1. A rotating casing is housed in a circular casing having an annular flow passage formed on the outer peripheral portion thereof, and a large number of blades are formed on the outer peripheral portion of the impeller at equal intervals in the circumferential direction. The gas is sucked into the vortex chamber formed between the blades through the inlet opening to the annular flow path, and the gas swirled and compressed in the vortex chamber is discharged to the outlet opening to the annular flow path. In the vortex flow blower, each of the blades is composed of a plate body that linearly projects from the plate surface of the impeller,
The inner and outer ends of each blade are formed so as to form a predetermined angle in a direction opposite to the impeller rotation direction with respect to a line extending from the center of rotation of the impeller, and the entire blade is concave in the impeller rotation direction. A swirl blower characterized by what it has done.