JPS61207890A - Fluid pressurizing device - Google Patents

Abstract

PURPOSE:To enable smoothening of the flow of fluid by a method wherein a distance to the inner peripheral surface, positioned opposite to the tip of a blade, of each of 2 casing is gradually decreased toward the axial center of a wheel, and the inner peripheral surface is formed so as to be curved inwardly. CONSTITUTION:A distance to inner peripheral surfaces 46 and 47, positioned facing tips 41 and 42 of a blade, of first and second casings 15 and 19, respectively, is gradually decreased toward an axial center 60 of a wheel 12, and the inner peripheral surfaces 46 and 47, positioned facing the tips 41 and 42 of the blade, are formed in a manner to be curved inwardly as seen from cutting in the direction of the axis. This enables enough lengthening of the length of a fluid seal, formed between a groove 40 and large parts 35, 36, without an increase in the size of the whole, and since the more the surface, positioned facing the tips of blades 13 and 14, of the casings 15 and 19 are spaced away from the wheel 12 in a manner to draw a curved line, the more the surface is spread, the fluid separated from the blades 13 and 14 is smoothly rotated within curved tunnels 17 and 20, resulting in improvement of efficiency.

Description

[Detailed Description of the Invention] [Field of Application of the Invention] The present invention relates to a fluid pressurizing device for a multi-tiered house.
In particular, it relates to a fluid pressurizing device called a vortex blower when gas is used as the fluid, and a Wesco type pump when liquid is used.

[Background of the invention]

Although the fluid pressurization device of this structure has a relatively simple structure, it can obtain a high discharge pressure, so it can be used as a fluid pressure generation source for pneumatic powder transportation or as a high-head pump. It is used.

Particularly recently, a multi-stage system that can obtain higher discharge pressure has been proposed. Examples of such systems include Utility Model Application No. 52-169109 and Utility Model Application No. 54-5.
What is shown in Japanese Patent No. 6210 is known.

The structure shown in these examples is such that the fluid pressurized in the first curved tunnel is guided into the second concave tunnel, where it is further pressurized.

That is, as shown in FIG. 11, there is a wheel 12 having a large number of blades 13 and 14 on both sides, and a first casing 15 and a second casing 19 located on both sides of the wheel. 13. A plane surrounding 14-
A curved tunnel 17 and a second curved tunnel 20 are formed.

The diameter of the gap between the first casing 15 and the second casing 19 is larger than the maximum diameter portion 35.36 of the arcuate portion 18.2□1 of the first and second curved tunnels 17°20. It has a large, inwardly opening groove into which the large-diameter portion 45 of the wheel 12, which extends further back than the tips 41 and 42 of the blades 13 and 14, is inserted.

However, in such a structure, the surfaces of the first casing 15 and the second casing 19 facing the blade tips 41 and 42 were parallel to the axis of rotation @7, so the second circular tunnel In many cases, fluid leaks from inside 20 into the first curved tunnel 17 through the gap between #4O and the large diameter part 45, and if high discharge pressure cannot be obtained, it is necessary to There was a drawback that the efficiency of the pressure device was reduced.

Of course, if the outer diameters of the first and second casings 15.19 are increased, #l! 40 and the large diameter portion 45 of the wheel 12
It is possible to increase the length of the seal between the .

[Purpose of the invention]

The present invention has been made in view of these points, and its purpose is to provide a highly efficient fluid pressurizing device that can obtain high discharge pressure without increasing the size. It's about doing.

[Summary of the invention]

That is, in the present invention, between the first casing and the second casing, the diameter from the rotation center to the bottom is larger than the maximum diameter part of the arcuate part of the first and second curved tunnels, It has a groove that opens inward, and the large diameter part of the wheel that protrudes beyond the tips of the vanes is inserted into this groove to provide a small pressure seal for the fluid passing through the first and second curved tunnels. When entering through a gap, the distance between the first casing and the second casing on the inner circumferential surface 1 facing the blade tip is k toward the axial center of the wheel.
The blade gradually becomes smaller, and when the inner circumferential surface facing the blade tip is cut in the axial direction, that portion is configured to curve inward. With this configuration, the length of the fluid seal formed between the groove and the large-diameter portion can be made sufficiently long without increasing the overall dimensions. The separated fluid rotates smoothly within the first and second curved tunnels, respectively, because the surfaces of the first and second casings facing the tips of the vanes are curved and spread out as they move away from the wheel.

This improves efficiency.

[Embodiments of the invention]

1 is a driving means. Although an engine, a hydraulic motor, etc. can be used as the driving means, this embodiment shows an example in which an electric motor is used.

This electric motor has a housing 2, in which a stator core 4 having #i and stator windings 3 is fixed. End brackets 5.6 are fixed to both ends of the housing 2, respectively.

The end brackets 5.6 are fixed. The end brackets 5.6 support one end of the rotating shaft 7 via bearings 8.9. A rotor core 10 is provided inside the stator core 4 and is fixed to the rotating shaft 7 through a gap.

A cooling fan 11 is installed on the rotary shaft 7 at a position outside the end bracket 5, and a wheel 12 is installed at a position outside the end bracket 6.
is the installation.

The wheel 12 has a large number of vanes 13 and 14 on both sides and around the rotation shaft 7, respectively.

The first casing 15 is located on one side of the wheel 12, and has blades 13 provided on one side of the wheel 12.
Together with the enclosure and the wheel 12, a first curved tunnel 17 is formed around the rotation center 16. This first curved tunnel 17 has a circular arc portion 1 centered on the rotation center 16 in the middle.
It has 8. The second casing 19 is located on the other side of the wheel 12, surrounds the blades 14 provided on the other side, and forms a second curved tunnel 20 around the rotation center 16 together with the wheel 12. There is. This second concave tunnel 20 has a circular arc shape s21 centered on the rotation center 16 in the middle.
have.

-IIIK of the first curved tunnel 17 is the first suction port 22
A first discharge port 23 is provided on the other side. A first partition wall 24 is provided between the first suction port 22 and the first discharge port 23.

A second suction port 25 is provided on one side of the second curved tunnel 20, and a second discharge port 26 is provided on the other side. A second intestinal tube 27 is located between the second suction port 25 and the second discharge port 26.
is the provision.

The first discharge port 23 and the second suction port 25 communicate through a communication path 28.

An inner spigot 30 centered on the first casing xsl/Cu rotation center 16 is provided, and the second casing 19 is provided with an outer spigot 31 that fits into the inner spigot 30. The first casing 15 and the second casing 19 are connected by bolts 32 as a fastening means, and both pilot 3
It is fastened so that the outside of 0.31 is in close contact.

Between the first casing 15 and the second casing 19,
The diameter from the center of rotation 16 to the L-bottom part 33 is larger than the maximum diameter part 35.36 of the arcuate part 18.21 of the first and second curved tunnels 17.20, and the diameter opens inward. 4
0 is provided 0 this 54oo feathers $13.14F)
The large diameter portion 45 of the wheel 12 that protrudes beyond the tips 41 and 42 (see FIG. 9) is connected to the first and second curved tunnels 17.
゜The first casing 15 and the second casing 19 each enter through a minute gap that serves to seal the pressure of the fluid passing through the inside of the casing 15, 19.
The distance between the blade tips 41 and 42 and the opposing inner circumferential surface 46 and 47 is the center 6 as seen in the axial direction of the wheel, and the distance gradually decreases by /J1 as you move towards OK.
When the inner circumferential surface 46° 47 facing 1.42 is viewed in the axial direction, it is configured to curve inward at that portion or ζ.

Vane 13iL passing through the first curved tunnel 17 first partition wall 2
4 and the timing when the blade 14 passes through the end 61 on the first discharge port 23 side, and the timing when the blade 14 passes through the second curved tunnel 20.
The blades 13 on both sides of the Mi-wheel 120 are arranged at different timings to pass through the end 62 of the wall 27 on the second discharge port 26 side.
．． 14 and the first bulkhead 24. By arranging the second partition wall 27, it is possible to lower the generated noise level.

This is because the noise is mainly lost when the wings a13, 14 pass through the ends 61, 62 of the first and second partitions 24, 27.

Therefore, by doing as described above, the blades 13.
14 is no longer constantly passing through the end portions 61 and 62, the noise generated can be reduced.

If, when the first casing 15 and the second casing 19 are assembled, the dimension from the ends 61 to 62 in the rotational direction is an integral multiple of the interval between adjacent blades 13 or ridges 140, As shown in FIG. 10, the blade 14. o They may be provided with a shifted phase.

The wheel 12 is engaged, as shown in FIG.
The first and second casings 15.19 each have an inner circumferential surface 65.66 centered on the center of one rotation 16 inside the blades 13 and 14, and a first inner circumferential surface 65.66. , have outer circumferential surfaces 71.72 which oppose each other through a small gap which serves to provide a pressure seal for the fluid passing through the second curved tunnel 17.20.

An rri silencer 73 is connected to the first suction port 22,
The electric motor is fixed to the ± of this silencer 73.

In order to enhance the cooling effect, the end bracket 6 is provided with an annular flange 74 centered on the rotation center 16 and a plurality of arms 75 extending in the axial direction from the side surface of the end bracket 6 and supporting the annular 7 flange 74. , the first casing 15 is fixed to the annular 7 flange 74 and the end bracket 6 is fixed.
This allows cooling air to pass between the side wall of the first casing 15 and the first casing 15.

The first casing 15u and the second casing 19 are formed by machining a hole 80 for passing the rotating shaft 7 therethrough and a fitting seat 81 that fits into the annular 7 flange 74 from a casting having the same shape as the second casing 19. As described above, the first casing 15 is provided with the inner spigot 30 and the second casing 19 is provided with the outer spigot 31 by cutting.

Note that 83 is a fan cover, and 84 is an arrow indicating the rotation direction of the wheel.

In the configuration as described above, when the wheel 12 is driven by the electric motor, the fluid passes through the silencer fj173, passes through the first suction port 22, and enters the first curved tunnel 17 K.
MIL gets into it 1. The fluid that has entered the first curved tunnel 17 is pressurized by the blades a13//c and heads toward the first discharge port 23. The first discharge port 23&C Kurimaru fluid passes through the communication path 28 and enters the second curved tunnel 20 from the second suction port 25□, where it is further pressurized and is transferred to the second discharge port 2.
It is discharged from 6.

By the way, the fluid is in the first I@two concave curved tunnel 1f 20
Inside, each blade moves as follows (o':) 13゜1
The fluid discharged from the tips 41, 42 of the blades 13, 19 flows along the inner wall surfaces of the first and second casings 15, 19, respectively, and reaches the sides 85, 86 of the other blades 13, 14. Also, biased by the respective vanes 13,14, the air flows along the vaned outer circumferential surface 87,88 of the wheel 12 and is ejected from the tips 41,42 of the respective vanes 13,14, so that the first casing 15 and the second casing 19, inner circumferential surfaces 46° 47 facing the blade tips 41, 42, respectively.
The distance at 1 is gradually reduced toward the axial center 60 of the wheel 12, and when viewed in the axial direction, the inner circumferential surface 46.47 opposing the blade tip 41.42 is curved inward. This configuration serves to smooth the flow of fluid within the first and second curved tunnels 17.20.

Furthermore, the length of the fluid seal formed between the groove 40 and the large diameter portion 45 can be made sufficiently long without increasing the overall size. According to the invention, between the first casing and the second casing, there is a groove that opens inward and has a diameter larger than the maximum diameter of the arcuate portion of the first and second curved tunnels, The large diameter part of the wheel, which also has the protruding tips of the blades, is inserted into this groove through a small gap that serves to seal the pressure of the fluid passing through the first and second curved tunnels. In this step, the distance between the first casing and the second casing at the inner circumferential surface 1 facing the blade tip is gradually reduced toward the axial center of the hose, and the distance is cut along the axial direction of the single rotation shaft. When viewed from above, the inner circumferential surface facing the blade tip is curved inward.

With this configuration, the length of the fluid seal formed between the groove and the large diameter portion can be made sufficiently long without increasing the overall diameter.

In addition, the surfaces of the first and second casings facing the blade tips are curved and spread out as they move away from the wheel, so the fluid that has left the tip of the blade spreads inside the first and second curved tunnels, respectively. Efficiency is improved due to smooth rotation.Furthermore, the fluid released from the tips of the vanes smoothly moves away from the seal along the curved inner circumferential surfaces of the first and second casings. Since it is guided, it works to make the seal between the groove and the large diameter part even more effective.

[Brief explanation of drawings]

FIG. 1 is a partially cutaway front view showing an embodiment of the fluid pressurizing device of the present invention, and FIG. 2 is a side view of the fluid pressurizing device shown in FIG.
Figure 3 is a side view of the first casing - Figure 4 is a side view of Figure 3.
- Figure 5 is a diagram cut along line A'.
- Figure 6 is a diagram cut along line B'.
7 is a side view of the second casing, FIG. 8 is a view of FIG. 7 cut along line A-A', and FIG. 9 is a side view of the second casing. Enlarged view of the main parts of Figure 1, No. 10
The figure shows a part of a developed view of the outer peripheral surface of the wheel, and FIG. 11 is a partially cutaway front view of a conventional fluid pressurizing device.
5 is the first casing, 16 is rotating 1[,%, 11 first curved tunnel, 18i arc shape & 19 is second casing, 20 is second curved tunnel, 21 is arc shape, 22Fi
First suction port, 23 first discharge ports, 24 is the first partition, 25
is the second suction port, 26d is the second discharge port, 27 is the second partition, 2
8I/'i slow path, 32 is a bolt showing an example of fastening means, 33 is the bottom fL 3536 is the thickest diameter fox 40 is #l-45
is the large diameter part. Part III with 11 cases of fluid pressurization device correction Patent applicant 6th name ts+o) Manufactured by Hitachi Co., Ltd.

Claims (1)

[Scope of Claims] 1. A wheel having a large number of blades on both sides and around the center of rotation, and a wheel located on one side of the wheel, the blades being provided on one side of the wheel. a first casing enclosing the wheel and forming, together with the wheel, a first curved tunnel around the center of rotation with an arcuate portion in the middle; a second casing surrounding the provided blade and forming, together with the wheel, a second curved tunnel having an arcuate portion in the middle around the rotation center;
a first suction port provided on one side of the first curved tunnel, a first discharge port provided on the other side, and a first partition wall formed between the first suction port and the first discharge port; a second suction port provided on one side of the second curved tunnel and a second discharge port provided on the other side;
A second partition wall formed between the second suction port and the second discharge port, a communication path that communicates the first discharge port and the second suction port, and the first casing and the second casing. and a driving means for rotationally driving the wheel around the rotation center, and a diameter between the first casing and the second casing is provided between the first casing and the second casing. has a groove that is larger than the maximum diameter of the arcuate portion of the first and second curved tunnels and opens inward, and the blade protrudes into the groove beyond the tip of the blade. in each of the first casing and the second casing, in which the large-diameter portion of the wheel enters through a small gap that serves to seal the pressure of the fluid passing through the first and second curved tunnels; The distance to the inner circumferential surface facing the blade tip is gradually reduced toward the axial center of the wheel, and when the inner circumferential surface facing the blade tip is cut in the axial direction, that part is A fluid pressurizing device characterized in that it is configured to curve inward. 2. The timing at which the blade passing through the first curved tunnel passes the end of the first partition wall on the first discharge port side, and the timing at which the blade passing through the second curved tunnel pass through the first discharge port side end of the first partition The blades on both sides of the wheel, the first partition wall, and the second partition wall are arranged so as to be different from the timing of passing the end of the second partition wall on the second discharge port side. The fluid pressurization device according to scope 1. 3. The wheel has inner circumferential surfaces on both sides that are centered on the rotation center inside the blades, and the first and second casings have inner circumferential surfaces and the first and second casings, respectively. 3. A fluid pressurizing device according to claim 1 or 2, characterized in that the fluid pressurizing device has outer circumferential surfaces facing each other via a small gap that serves to pressure seal the fluid passing through the curved tunnel.