JPH07117057B2 - Fluid pressurizer - Google Patents

Description

Description: FIELD OF THE INVENTION The present invention relates to a multi-stage fluid pressurizing device, and is particularly called a vortex blower when a gas is used as a fluid, and is used when a liquid is used. Wesco Type
The present invention relates to a fluid pressure device called a pump.

BACKGROUND OF THE INVENTION A fluid pressurizing device of this type can obtain a high discharge pressure even though its structure is relatively simple. Therefore, a fluid pressure generating source for powder transportation by air and a high lift are provided. It is often used as a pump.

In particular, recently, there has been proposed a multi-stage type that can obtain a higher discharge pressure. As such examples, those disclosed in Japanese Utility Model Publication No. 52-169109 and Japanese Utility Model Publication No. 54-56210 are known.

The structure shown in these figures has a structure in which the fluid pressurized in the first curved tunnel is guided into the second curved tunnel and further pressurized therein.

That is, as shown in FIG. 11, 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 in the axial direction of the wheel 12, respectively. Form a first curved tunnel 17 and a second curved tunnel 20 surrounding the blades 13 and 14, respectively.

Further, between the first casing 15 and the second casing 19, a groove 40 having a diameter larger than the maximum diameter portion in the first and second curved tunnels 17 and 20 and opening inward is provided. The large diameter portion 45 of the wheel 12 protruding from the tips 41 and 42 of the blades 13 and 14 is inserted into the groove 40.

However, with such a structure, the first casing 15
Since the inner wall surfaces of the second casing 19 and the blade tips 41, 42 facing each other were parallel to the axis of the drive shaft 7, from the second curved tunnel 20 to the first curved tunnel 17, Groove 40
As a result of the fluid leaking through the gap between the large diameter portion 45 and the large diameter portion 45, the efficiency of the fluid pressurizing device is reduced. However, if the outer diameters of the first and second casings 15 and 19 are increased, the length of the seal between the groove 40 and the large diameter portion 45 of the wheel 12 can be increased, and leakage can be reduced. Although possible, this is, of course, undesirable because it adds to the overall size of the device.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned problems of the prior art, and an object of the present invention is to provide a fluid pressurizing device capable of obtaining a high discharge pressure without increasing the size and having a high efficiency. To provide.

[Summary of the Invention] In the present invention, a wheel includes an inner peripheral wall formed on both side portions on an inner peripheral side of each blade along the axial direction, and an inter-blade space is further formed on an inner peripheral portion of each inner peripheral wall. A thin wall portion having a thickness smaller than the dimension of each of the first and second casings, and each of the first and second casings has an overhanging projection protruding at a position corresponding to the inner peripheral surface of the wheel and the thin wall portion with a minute gap therebetween. , The inner circumferential surface of the first and second casings facing the respective blades in the first curved tunnel and the second curved tunnel, the distance from the blade tip gradually decreases toward the axial center of the wheel, A space with a circular cross section between the first and second curved tunnels and the side where the blades of the wheel are provided, with the tip extending along the large diameter part of the wheel and forming a curved projection so as to extend in the centripetal direction. To define
This has achieved the above-mentioned object.

[Embodiment of the Invention] An embodiment of the present invention will be described below with reference to FIGS. 1 to 10. 1 to 10, the same reference numerals as in FIG. 11 represent the same or corresponding ones.

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

The electric motor 1 has a housing 2, and a stator core 4 having a stator winding 3 is fixed in the housing 2. End brackets 5 and 6 are fixed to both ends of the housing 2, respectively.

The end brackets 5 and 6 support one end sides of the drive shafts 7 via bearings 8 and 9, respectively. A rotor core 10 fixed to the drive shaft 7 is provided inside the stator core 4 with a gap.

A cooling fan 11 is attached to a position of the drive shaft 7 projecting outward from the end bracket 5, and a wheel 12 is attached to a position projecting outward of the end bracket 6.

The wheel 12 has a large number of blades 13 and 14 on both sides in the axial direction. The first casing 15 is located on one side of the wheel 12 as shown in FIGS. 1 and 9, and surrounds the blade 13 provided on one side of the wheel 12,
Together with 12, the first curved tunnel 17 is formed. This first curved tunnel 17 is an arc-shaped space centered on the center of rotation 16.
Has 18. The second casing 19 is shown in FIGS.
As shown in the drawing, it is located on the other side of the wheel 12, surrounds the blade 14 provided on the other side, and forms a second curved tunnel 20 together with the wheel 12. This second curved tunnel
20 has an arcuate space 21 centered on the center of rotation 16.

In the first casing 15, a first suction port 22 is provided at one end of the first curved tunnel 17 as shown in FIGS. 1 and 3, and a first discharge port 23 is provided at the other end. It is provided. In addition, the first suction port 22 and the first discharge port 23 of the first curved tunnel 17
A first partition 24 is provided between them.

In the second casing 19, a second suction port 25 is provided at one end of the second curved tunnel 20 as shown in FIGS. 1, 2, and 7, and a second suction port 25 is provided at the other end. A discharge port 26 is provided. A second partition 27 is provided between the second suction port 25 and the second discharge port 26 of the second curved tunnel 20. And
A communication passage 28 is formed between the first discharge port 23 of the first casing 15 and the second suction port 25 of the second casing 19.
By 28, both 23 and 25 communicate with each other.

The first casing 15 is provided with an inner spigot 30 centered on the center of rotation 16, and the second casing 19 is provided with an outer spigot 31 that fits with the inner spigot 30. Then, the first casing 15 and the second casing 19 are fastened with bolts 32 as fastening means so that the outer peripheral sides of both inlays 30 and 31 come into close contact with each other.

Between the first casing 15 and the second casing 19, the inner wall portion facing the large diameter portion 45 of the wheel 12 described later,
A groove 40 that is centered on the rotation center 16 and has a diameter up to the bottom 33 that is larger than the maximum diameter portions 35 and 36 of the arcuate portions 18 and 21 of the first and second curved tunnels 17 and 20 and that opens inward. Is provided. This groove
As shown in FIG. 9, some of the blades 40 have tips 41, 42 of the blades 13, 14.
The larger-diameter portion 45 of the wheel 12, which is more projecting, is entered through a small gap that serves for pressure sealing of the fluid passing through the first and second curved tunnels 17,20. Therefore, the wheel 12 is located between the respective blades 13 and 14, and has an outer circumference having a larger diameter than the respective blades 13 and 14, and a thickness smaller than the dimension between the respective blades 13 and 14 in the axial direction. It has the large diameter portion 45.

In each of the first casing 15 and the second casing 19,
On the inner peripheral surface portions of the first curved tunnel 17 and the second curved tunnel 20 facing the respective blade tips 41, 42, as the distance between the blade tips 41, 42 approaches the axial center 60 of the wheel 12. Curved projections 46 and 47 are formed so as to be gradually smaller, and the tips thereof protrude along the large diameter portion 45 and in the centripetal direction. That is, as shown in FIG. 9, each of the protrusions 46 and 47 has one end side surface on the axial center side 60 along the large diameter portion 45 of the wheel 12 and is extended continuously with the groove 40. Formed,
In addition, the other side surface of the tip opposite to the axial center side 60 is connected to the inner peripheral surfaces of the first and second curved tunnels 17 and 20, and faces the side portions 87 and 88 of the blades 13 and 14, respectively. It has a curved shape. Therefore, as shown in FIG. 9 by the projections 46 and 47, the side portions 87 and 88 of the wheel 12 provided with the blades 13 and 14 and the first and second curved tunnels 17 and 20 have a substantially circular cross-section space. Defined (not shown).

Further, the timing when the blade 13 of the wheel 12 passes through the end 61 of the first partition wall 24 on the first discharge port 23 side in the first curved tunnel 17, and the blade 14 of the wheel 12 is the second curved tunnel.
If the blades 13, 14 and the first partition wall 24, the second partition wall 27 are arranged so that they differ from the timing of passing through the end 62 of the second partition wall 27 on the second discharge port 26 side within 20, the generated noise level Can be lowered.

The reason is that the noise is mainly due to the blades 13 and 14 being the first and second partition walls 2
It occurs when passing the ends 61 and 62 of 4,27. Therefore, by doing as described above, the blades 13 and 14 have the end portions 61,
Since it does not pass through 62 at the same time, the generated noise can be reduced.

If the first casing 15 and the second casing 19 are assembled, the dimension from the end portions 61 to 62 in the rotation direction is
When the interval between the adjacent blades 13 or 14 is an integral multiple, the phase of the blade 14 may be shifted with respect to the blade 13 as shown in FIG.

Further, the wheel 12 has blades 13,1 as shown in FIG.
Inner peripheral walls 65, 66 are formed along both sides of the inner peripheral side of the side portions 87, 88 along the axial direction.Furthermore, in the axial direction between the inner peripheral walls 65, 66, the respective blade gaps 13, A thin portion 67 having a thickness smaller than the dimension between 14 is formed in the centripetal direction.

On the other hand, each of the first casing 15 and the second casing 19 is
Overhanging protrusions 71, 71 protruding at a position corresponding to the inner peripheral walls 65, 66 and the thin portion 67 of the wheel 12 through a minute gap that serves for pressure sealing of fluid passing through the first and second curved tunnels 17, 20. 72 is formed in the axial direction.

Returning to FIG. 1 again, a muffler 73 is connected to the first suction port 22 of the first casing 15, and the motor 1 has this muffler.
It is fixed on 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 flange 74. The first casing 15 is fixed to the annular flange 74 so that cooling air can pass between the side wall of the end bracket 6 and the first casing 15.

Furthermore, the first casing 15 is formed by cutting a hole 80 for passing the drive shaft 7 from a casting having the same shape as the second casing 19 and a fitting seat 81 for fitting with the annular flange 74 by cutting. Also, the inner spigot 30 provided in the first casing 15,
The outer inlay 31 provided on the second casing 19 is formed by cutting. In addition, in FIG.
Reference numeral 83 is a fan cover, and reference numeral 84 in FIG. 2 is an arrow indicating the rotation direction of the wheel 12.

When the wheel 12 is driven by the electric motor 1 in the structure configured as described above, the fluid passes through the muffling device 73 and is taken into the first curved tunnel 17 through the first suction port 22. The fluid entering the first curved tunnel 17 is
It is pressurized by 13 and goes toward the first discharge port 23. The fluid coming to the first discharge port 23 passes through the communication passage 28 and enters the second curved tunnel 20 from the second suction port 25. Then, it is further pressurized here and discharged from the second discharge port 26.

By the way, the fluid moves in the first and second curved tunnels 17 and 20 as follows. That is, the fluid discharged from the tips 41 and 42 of the blades 13 and 14 flows along the inner wall surfaces of the first and second casings 15 and 19, and the ends 85 and 85 of the other blades 13 and 14, respectively. Up to 86. Here again urged by the respective wings 13,14,
It flows along the bladed sides 87, 88 of the wheel 12 and is emitted from the tips 41, 42 of the respective blades 13, 14. Therefore, the projections 46, 47 provided on the inner peripheral surface portion corresponding to the blade tips 41, 42 of the first casing 15 and the second casing 19 are the blade tips 41, 42.
The distance between the wheel 12 and the wheel 12 becomes gradually smaller toward the axial center 60, and the tip projects along the large diameter portion 45 and extends in the centripetal direction to form a curved shape.
Since the side portions 85 and 86 provided with the vanes 13 and 14 and the first and second curved tunnels 17 and 20 can define a space having a substantially circular cross section, the flow of the fluid passing through the circular cross section. Has the function of smoothing

Further, by forming the protrusions 46, 47 as described above, the entire length of the groove 40 between the first and second casings 15, 19 and the large diameter portion 45 of the wheel 12 can be increased, so that the wheel 12 itself. The length of the fluid seal between the large-diameter portion 45 and the groove 40 can be made sufficiently long without increasing the diameter, and therefore, the sealing effect between the low pressure side and the high pressure side can be improved and the entire device can be improved. It becomes unnecessary to increase the dimension of. Moreover, as compared with the conventional example, since the thin portion 67 is provided on the wheel 12, the wheel can be quantified.

Furthermore, not only can the length of the fluid seal formed between the groove 40 and the large diameter portion 45 be made sufficiently long, but it is also formed between the overhanging projections 71, 72 and the inner peripheral surfaces 66, 67. Since the length of the fluid seal to be used can be made sufficiently long, the airtightness of the first curved tunnel 17 and the second curved tunnel 20 can also be increased, and as a result, the sealing effect between the low pressure side and the high pressure side can be improved. Improve further.

[Advantages of the Invention] As described above, according to the present invention, the distance between the blade tip and the inner peripheral surface of the first curved tunnel and the second curved tunnel is opposite to the axial direction of the wheel. It becomes smaller toward the center and has a curved projection so that the tip extends in the centripetal direction along the large diameter part of the wheel, and the side part where the blade of the wheel is installed and the first and second curved tunnels. Since it is configured to define a space with a substantially circular cross section, it has the effect of smoothing the flow of fluid, and the length of the entire groove between the large diameter parts of the first and second casings and the wheel. By increasing the size of the wheel, the length of the fluid seal between the large diameter portion of the wheel and the grooves of the first and second casings can be made sufficiently long without increasing the size of the wheel itself, and the size of the entire device can be increased. When no longer needed In both cases, the sealing effect between the low pressure side and the high pressure side can be improved, and the wheel can be quantified.

In addition, inner peripheral walls are formed on both sides on the inner peripheral side of each blade along the axial direction, and a thin portion having a thickness smaller than the dimension between the respective blades is formed further on the inner peripheral portion than each inner peripheral wall. However, in each of the first and second casings, since the protrusions are formed at positions corresponding to the inner peripheral surface and the thin portion of the wheel with a minute gap therebetween, the above-mentioned groove is formed. Not only can the length of the fluid seal with the large-diameter portion be made sufficiently long, but also the length of the fluid seal formed between the overhanging protrusions of the first and second casings and the inner peripheral surface of the wheel can be made sufficiently long. You can
Therefore, the first curved tunnel and the second curved tunnel can be reliably separated from each other, and there is an effect that the sealing property between the low pressure side and the high pressure side can be further improved.

[Brief description of drawings]

FIG. 1 is a partially cut front view showing an embodiment of a fluid pressurizing apparatus of the present invention, FIG. 2 is a side view of the fluid pressurizing apparatus shown in FIG. 1, and FIG. 3 is a side surface of a first casing. 4 and 5 are sectional views taken along the line AA 'in FIG. 3, and FIG.
6 is a sectional view taken along the line B ', and FIG.
FIG. 7 is a side view of the second casing, FIG. 8 is a sectional view taken along the line AA ′ of FIG. 7, and FIG. 9 is an enlarged sectional view of an essential part of FIG. 1. FIG. 10 is a partially developed view showing the outer peripheral surface of the wheel, and FIG. 11 is a partially cut sectional view of a conventional fluid pressure device. DESCRIPTION OF SYMBOLS 1 ... Drive means, 7 ... Drive shaft, 12 ... Wheel, 13,14 ... Blade, 15 ... First casing, 16 ... Rotation center, 17 ... First curved tunnel, 19 ... Second casing, 20 ... Second bend -Shaped tunnel, 22 ... First suction port, 23 ... First discharge port, 24 ... First partition wall,
25 ... second suction port, 26 ... second discharge port, 27 ... second partition, 28 ...
Communication passage, 32 ... bolt, 33 ... bottom, 35,36 ... maximum diameter, 40
… Grooves, 45… Large diameter part, 46, 47… Protrusions, 65, 66… Inner peripheral wall, 67…
Thin part, 71,72… Overhanging protrusion, 85,86… side part.

Continuation of front page (56) References: Showa 50-148603 (JP, U) Showa 52-169109 (JP, U) Showa 54-56210 (JP, U)

Claims (2)

[Claims] 1. A wheel mounted on a drive shaft, each wheel being located on both sides in the axial direction and having a plurality of blades arranged in a circumferential direction orthogonal to the axial direction, and a wheel in the axial direction of the wheel. A first casing and a second casing, which are fastened and fixed to each other on both sides, surround the wheel, and form a first curved tunnel and a second curved tunnel respectively with the side portions of the wheel provided with the respective vanes. The wheel has a large-diameter portion located between the blades in the axial direction and having an outer periphery having a diameter larger than that of the blades, and the first casing is formed at one end of the first curved tunnel. Has a first suction port, a first discharge port formed at the other end of the first curved tunnel, and a first partition wall formed between the first suction port and the first discharge port. , The second casing of the second curved tunnel A second suction port formed at the end, a second discharge port formed at the other end of the second curved tunnel, and a second partition wall formed between the second suction port and the second discharge port. And an inner wall portion that forms a communication path between the first discharge port of the first casing and the second suction port of the second casing, and that faces the large-diameter wheel portion between the first casing and the second casing. In the fluid pressurizing device having a groove that opens inwardly and that separates a minute gap from the large diameter portion of the wheel, the wheel has an inner peripheral wall on both sides on the inner peripheral side of the side portions of the respective blades. And a thin wall portion having a thickness smaller than the dimension between the respective blades is formed between the inner peripheral walls in the axial direction in the centripetal direction. The inner peripheral wall and the thin portion are located at positions corresponding to the inner peripheral wall and the thin portion. An overhanging protrusion is formed in the axial direction to overhang a minute gap, while the inner circumferential surface of the first curved tunnel and the second curved tunnel facing the respective blades has one side surface on the axial center side. Along the large diameter portion of the wheel and connected to the groove, and the other side surface of the tip opposite to the axial center side is connected to the inner peripheral surface portions of the first and second curved tunnels. A fluid pressurization characterized by forming a curved projection toward the side of the blade, and defining a space with a substantially circular cross section between the first and second curved tunnels and the side of the wheel where the blade is provided. apparatus. 2. The timing when the blade passing through the first curved tunnel passes through the end of the first partition on the first discharge port side, and the timing when the blade passes through the second curved tunnel. 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 pressurizing device according to claim 1.