JPH0299794A - Eddy current type turbomachinery - Google Patents

Abstract

PURPOSE:To increase the compression ratio and improve the compression efficiency by installing an annular guide member in a main flow passage and connecting the inner peripheral side surface and the outer peripheral side surface of the guide member by a corner part and reducing the sectional area of the guide member on a discharge port side. CONSTITUTION:Since an annular guide member 4 is installed in a main flow passage 24, fluid smoothly flows in swirl form. Since the inner peripheral side surface 4a and the outer peripheral side surface 4b of the guide member 4 are connected by a corner part 4c having a prescribed radius of curvature, generation of turbulent flow of fluid on the peripheral surface of the guide member 4 is prevented, and a smooth flow is generated. Further, since the sectional area of the guide member 4 is reduced on a discharge port 62 side, the sectional area of the main flow passage 24 is increased as the fluid is compressed, and the smooth flow of fluid is obtained. Therefore, the compression ratio can be increased, and the compression efficiency can be improved.

Description

Detailed Description of the Invention (Industrial Field of Application) The present invention applies to swirl-type vacuum pumps, compressors, turbines, etc., which give a spiral motion to a fluid by rotating an impeller and convert this angular kinetic energy into pressure. This invention relates to improvements in vortex type turbomachinery.

(Prior Art) Conventionally, this type of vortex type turbomachine has been equipped with an impeller having a large number of blades rotatably in a housing, as disclosed in Japanese Utility Model Application Publication No. 56-76188, for example. The impeller is rotated by the drive of the drive motor, the fluid is sucked into the main channel in the housing from the suction port of the housing, and the fluid is transferred in the main channel while being spirally moved in the axial direction of the main channel. It is known that the fuel is compressed while being compressed, and is discharged from the discharge port to the outside of the housing.

As shown in FIG. 10, the impeller in this whirlpool turbomachine has a large number of blades (c) on the outer peripheral surface (b) of the hub (a).
) extend radially, and the vanes (c) face the main flow path (e) within the housing (d). The blade (C) is formed in a fan shape extending from the front surface of the hub (a) to the outer peripheral surface of the rear end, and fluid flows into the blade (c) from the root of the blade leading edge (f), The flow follows the arc surface of the hub's outer circumferential surface (b), flows out from the outer circumference which is the trailing edge (g) of the blade, and flows in again from the root of the leading edge (f) of the blade, repeating this action to create a spiral movement. I will do it.

(Problem to be Solved by the Invention) However, in the above-mentioned vortex type turbomachine, since the blades 1t(c) of the impeller are simply exposed in the main flow path (e), the fluid does not flow into the main flow path. (e) It was difficult to perform a smooth spiral motion, and there were problems in that high angular kinetic energy could not be obtained and the pressure ratio was low.

Therefore, an annular guide member is provided in the main flow path (e),
It is conceivable for the fluid to move helically around the guide member. However, if the guide member is simply provided, turbulent flow will occur on the circumferential surface of the guide member, and even though the fluid pressure will be high on the outlet side, the main flow path (e) will not be adjusted according to the pressure state. There are problems such as the inability to obtain a cross-sectional shape. As a result, the fluid does not move in a sufficiently smooth spiral motion, resulting in an insufficient increase in pressure ratio.

The present invention has been made in view of the above, and by making the annular guide member have a smooth approximately semi-elliptical cross section and tapering it toward the discharge port, the fluid can move smoothly in a spiral manner and generate high pressure. The purpose is to obtain a ratio.

(Means for Solving the Problems) In order to achieve the above object, the means taken by the present invention are as shown in FIGS. 1 to 3.
) and a discharge port (62), and a housing (2) having a hollow annular portion (23) forming a main fluid passage (24). Furthermore, the housing (
2) includes a plurality of blades facing the main flow path (24).
32).

(32), . . . are formed, and the suction port (61) is formed.
) into the main flow path (24), the fluid is compressed while being transferred spirally, and is then discharged from the discharge port (62) into the main flow path (24).
) An impeller (3) for discharging the fluid to the outside is housed therein, and an annular guide member (4) for guiding the spiral movement of the fluid is disposed approximately on the central axis of the main flow path (24). The target is turbomachinery.

The annular guide member (4) is formed so that its cross-sectional area gradually decreases from the suction port (61) side to the discharge port (62) side, and the annular guide member (4) has a cross-sectional shape. Close to the tip of the blade (32), there is a flat inner peripheral side surface (4a) whose width corresponds to the chord length of the blade (32) and a substantially U-shaped outer peripheral side surface (4b), which is approximately half long. It is formed in a circular shape. In addition, the inner circumferential side surface (4a) and the outer circumferential side surface (4b) have an arcuate corner portion (4
c), connected via (4c), the corner (4c);
(4c) is the corner portion (
The ratio (R/D) of the radius of curvature (R) of 4c) is approximately 0.0
The configuration is such that the number is 2 or more.

(Function) With the above configuration, in the present invention, when the impeller (3) is rotated, fluid is sucked into the main channel (24) from the suction port (61), and the blades are disposed in the main channel (24). It flows into the blade (32) from the leading edge of the blade (32), flows out from the trailing edge, rotates in the main channel (24), and flows into the blade (32) again. The fluid then moves in a spiral along the annular guide member (4), obtains angular kinetic energy from the vanes (32) and flows in the axial direction of the main channel (24) while rotating, and is compressed by this spiral movement. It is discharged to the outside of the housing (2) from the discharge port (62).

(Effects of the Invention) Therefore, according to the vortex type turbomachine of the present invention, since the annular guide member (4) is provided in the main flow path (24), the fluid moves smoothly in a spiral manner, so that the compression ratio can be reduced. can be improved. Furthermore, since the inner circumferential side surface (4a) and the outer circumferential side surface (4b) of the guide member (4) are connected by the corner portions (4c), (4c) having a predetermined radius of curvature,
Since the fluid flows smoothly along the circumferential surface of the guide member (4) without causing turbulence, the spiral motion can be promoted more smoothly and the compression efficiency can be further improved. . In addition, the above guide member (4
) was made smaller on the discharge port (62) side,
As the fluid is compressed, the cross-sectional area of the main channel (24) becomes larger, the fluid flow becomes smoother, and the compression efficiency can be further improved.

(Example) Hereinafter, an example of the present invention will be described in detail based on the drawings.

As shown in FIGS. 1 and 2, (1) is a compression pump as a vortex type turbomachine, which compresses and discharges various fluids such as gas while transferring them in a spiral shape.

The compression pump (1) has an impeller (3) in a housing (2).
) is housed therein, and the housing (2) is formed by integrally combining a first housing member (21) and a second housing member (22), which are divided into left and right parts in FIG. has been done. and both housing members (21).

(22) includes disk portions (21a) and (22a) that cover both end surfaces of the impeller (3), and the disk portion (21a) and (22a).
a), a semi-torus part (21b) that is continuously formed on the outer peripheral edge of (22a) and has four semicircular annular parts;
22b), and the two half-torus parts (21b), (
22b) forms a hollow annular portion (23), and the inside of the central annular portion (23) is configured as a main fluid passage (24).

An annular guide member (4) for guiding the flow of fluid is disposed in the main channel (24) in the hollow annular part (23), and a guide member ( 4
) is provided with a stripper member (5) having a predetermined width extending over the outer circumferential surface of the guide member (4), and supports the guide member (4).
The main flow path (24) is divided into a high pressure side and a low pressure side. A guide path (51) through which the impeller (3) passes is cut in the inner circumferential portion of the stripper member (5), and a guide path (51) is cut out on the inner circumferential portion of the stripper member (5). )
is the half-torus part (2l) of the first housing member (21).
A fluid suction port (61) is provided in b), and a fluid discharge port (62) is provided in the half-torus portion (22b) of the second housing member (22) on the other side (left side in FIG. 2). The fluid introduced from the suction port (61) and the fluid discharged from the discharge port (62) are connected to the stripper member (
5) to prevent them from merging.

Further, the impeller (3) is configured by a plurality of blades (32) extending radially on the outer peripheral surface (31a) of a disc-shaped hub (31). Both end surfaces of the hub (31) are connected to the disk portions (21) of the housing members (21) and (22).
a), (22a) are closely covered and the hub (3
A drive shaft (7) is connected to the center of the drive shaft (1). The drive shaft (7) is located concentrically with the main channel (24) and the guide member (4), passes through the disk portion <22a) of the second housing member (22), and has an outer end (not shown). A motor is connected to the impeller (
3) is designed to rotate. Further, the hub outer circumferential surface (31a) is formed as a cylindrical surface concentric with the drive shaft (7), and constitutes a part of the outer 14 surface of the main flow path (24).

The blades (32) of the impeller (3), as shown in FIG. 31
) is formed across both end faces of the airfoil, and is also formed, for example, between airfoils that have a predetermined curvature a. Further, the blade (32) has a leading edge (32a), a trailing edge (32b), and a tip (
32c) is formed in a straight line and has a rectangular shape when viewed from the front, and when the fluid passes from the leading edge (32a) to the trailing edge (32b) of the blade, it passes from the front surface to the rear surface of the hub (31). The fluid is configured so that the flow when it passes through the vanes (32) becomes a substantially axial flow, and angular kinetic energy is imparted to the fluid when it passes through the vanes (32).

On the other hand, as shown in FIGS. 4 and 5, the annular guide member (4) is provided approximately on the central axis of the main flow path (24), and has a straight inner circumferential side surface (4a). The cross section is formed into a substantially semi-elliptical shape by the U-shaped outer peripheral side surface (4b). The inner circumferential side surface (4a) is close to the blade tip (32c) of the impeller (3), is formed linearly in cross section following the blade tip (32c), and has a width similar to that of the blade (32c). 32) is formed to have the same chord length. Both ends of the inner circumferential side surface (4a) are arcuate corner portions (4c);
The outer circumferential side (4b) is connected to the corner (4c) through the corner (4c), and the radius of curvature (R) of the corner (4c) is set to be 4 mm.

In other words, the corner portion (4c) is the outer diameter (D) of the impeller (3).
), and the ratio (R/D) of the radius of curvature (R) to the outer diameter (D) of this impeller is set to 0.02 or more. ) is 150
1, the radius of curvature (R) of the corner portion (4c) is set to be slightly larger than <31111B as described above.

Furthermore, the guide member (4) has a cross-sectional area equal to that of the suction port (61).
) side toward the discharge port (62) side. Specifically, Fig. 5 (a), (b
), (c), and (d), the length in the minor axis direction (4Y) is set to 16 mm, the radius of curvature (4R) of the outer circumferential side surface (4b) is set to 8fflI11, and the corner portion (4c) , (4c) is formed in a constant shape over the entire circumference, while the length in the major axis direction (4 22rarx, 20mm, 15+n as it progresses
m, 14+u+.

Further, on the outer circumferential side surface (4b) of the guide member (4), a plurality of support pieces (41), (4
1), ... are provided protrudingly at predetermined intervals, and the supporting pieces (
41), (41), ... are fitted into the hollow annular part (23), the guide member (4) is supported, and the guide member (4) and the hollow annular part (23
) is the main flow path (24).

In Fig. 6, the width of the inner circumferential side surface (4a') is larger than the chord length of the blade (32), that is, the length in the short axis direction is increased, and the corner portion (4c), (4c) and other configurations are the same as those shown in FIG. 5.

Next, the compression operation of this compression pump (1) will be explained.

First, when the motor is driven to rotate the drive shaft (7), the impeller (3) rotates within the housing (2), and each blade (3) rotates.
2), (32), . . . rotate within the main channel (24). On the other hand, fluid is sucked into the main channel (24) in the housing (2) through the suction port (61), flows into the blade (32) through the blade leading edge (32a), and flows into the blade (32) through the blade leading edge (32a).
2b), the vane (32) imparts angular kinetic energy to the fluid, which causes it to rotate around the guide member (4) and enter the vane (32) again. Then, the fluid is transferred in the axial direction of the main channel (24) while repeating the above-mentioned rotation, is compressed by spiral movement, and is discharged from the discharge port (62) into the housing (2).

In particular, the guide member (4) is formed such that the corner portion (4c) is formed in an arc shape with a radius of curvature (R) of 4111111, and the cross-sectional area becomes smaller toward the discharge port (62). As a result, the fluid moves smoothly in a spiral manner. That is, Figures 7 and 8 are similar to Figures 3 and 6.
The corner part (4d) is formed into a sharp edge shape corresponding to the figure, and in this case, when the fluid passes through the corner part (4d), as shown in FIGS. 7 and 8 (A), Inner peripheral surface (4a)
, (4a') or the outer circumferential surface (4b). Since the vortex flow of the fluid is obstructed by this turbulence, etc., the corner portion (4c
) is formed in an arc shape.

FIG. 9 shows the corner portion (4
c) shows the relationship between the ratio (R/D) of the radius of curvature (R) and the pressure ratio (△p) at the cutoff point, and this pressure ratio (8P
) increases rapidly when the ratio (R/D) approaches 0°02, meaning that turbulence and the like will no longer occur and the fluid will flow smoothly. Therefore, in this embodiment, the corner portion (4c) is formed with a radius of curvature of 41I11.

Therefore, since the annular guide member (4) is provided in the main flow path (24), the fluid moves smoothly in a spiral manner, and the compression ratio can be improved. Furthermore, since the inner circumferential side surface (4a) and the outer circumferential side surface (4b) of the guide member (4) are connected by the corner portions (4c), (4c) having a predetermined radius of curvature, the fluid flows into the guide member (4). ) will flow smoothly without causing turbulence or the like along the circumferential surface of the cylinder, the spiral motion can be promoted more smoothly, and the compression efficiency can be further improved. In addition, since the cross-sectional area of the guide member (4) is made smaller on the discharge port (62) side, as the fluid is compressed, the main channel (2)
4) The cross-sectional area becomes larger, and the fluid flow becomes smoother.
Furthermore, compression efficiency can be improved.

In addition, although this embodiment has been explained about the compression pump (1),
The present invention can be applied to various types of vortex type turbomachines such as turbines.

[Brief explanation of drawings]

1 to 9 show embodiments of the present invention, in which FIG. 1 is a longitudinal cross-sectional view of a compression pump, and FIG. 2 is a cross-sectional view taken along the line ■-■ in FIG. 1. Figure 3 is an enlarged sectional view of the main flow path, Figure 4 is a plan view of the annular guide member, Figures 5 (a), (b),
(c) and (d) are lines a-a and b- in Figure 4, respectively.
6 is an enlarged sectional view of the main flow path showing another annular guide member. 7 and 8 are enlarged cross-sectional views of the main flow path of the reservoir to explain the guide members of FIGS. 3 and 6, and FIG. 9 is the pressure ratio to the ratio of the outer diameter of the impeller and the radius of curvature of the corner portion. FIG. FIG. 10 is a sectional view of the main parts of a conventional vortex type turbomachine. (1)...Compression pump, (2)...Housing, (
3)... Impeller, (4)... Annular guide member, (4
a), (4a')... Inner peripheral side, (4b)... Outer circumferential road surface, (4c)... Corner, (5)... Stripper member, (23)... Center Annular part, (24)... Main channel, (32)... Vane, (32c)... Tip, (
61)...Suction port, (62)...Discharge port. Patent applicant Agent: Daikin Industries, Ltd.
Person Patent Attorney 1) Hiroshi and 2 others

Claims (1)

[Claims] (1) A housing (2) having a hollow annular portion (23) having a fluid suction port (61) and a fluid discharge port (62) and forming a main fluid channel (24); ), and facing the main flow path (24), a plurality of blades (32), (32),...
・ is formed, and the main flow path (
24); an impeller (3) that spirally transfers and compresses the fluid that has flowed into the fluid passageway (24), and discharges the fluid out of the housing (2) from the discharge port (62); This is a vortex type turbomachine equipped with an annular guide member (4) arranged to guide the spiral movement of fluid, the annular guide member (4) extending from the suction port (61) side to the discharge port (62). ) side, and the annular guide member (4) is formed so that its cross-sectional shape is close to the tip of the blade (32) and has at least the width of the blade (32). Flat inner side surface corresponding to the string length (
4a) and a substantially U-shaped outer circumferential side surface (4b), and the inner circumferential side surface (4a) and outer circumferential side surface (4b) have arc-shaped corner portions (4c), (4c). ), and the corner part (
4c) and (4c) are set so that the ratio (R/D) of the radius of curvature (R) of the corner portion (4c) to the outer diameter (D) of the impeller (3) is approximately 0.02 or more. A vortex type turbomachine characterized by: