JPS6353396B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a whirlpool pump, and particularly to a whirlpool pump that is intended to improve its water absorption performance.

Conventionally, in this type of vortex pump, air bubbles generated in the vortex waterway during self-priming operation,
There is a problem in that air bubbles due to cavitation generated during high suction return from the discharge side to the suction side and expand, significantly reducing the performance of the pump. However, it could not be said that it was completely satisfactory in this respect.

The present invention prevents and eliminates the disadvantages of the conventional technology or the previously developed technology,
The object of the present invention is to provide a vortex flow pump having stable water absorption performance.

The configuration of the vortex pump of the present invention includes a disc-shaped impeller having a plurality of vortex chambers each having a substantially semicircular cross section on its side surface and a blade section formed of blades, and a cross section provided opposite to the blade section. In a whirlpool pump comprising a substantially semicircular whirlpool waterway, the whirlpool waterway is partially formed on its discharge side so that the curvature of its outer corner is larger than the curvature of its inner corner. , the outer channel cross-sectional area is smaller than the inner channel cross-sectional area.

Next, before describing embodiments according to the present invention, the previously developed vortex flow pump will first be described with reference to the respective figures for ease of understanding.

Here, Fig. 1 is a longitudinal sectional view of the previously developed swirl pump, Fig. 2 is a sectional view taken along the - line in Fig. 1, and Fig. 3 is a sectional view taken along the - line in Fig. 1. A cross-sectional view, FIG. 4 is a perspective view of the casing cover, FIG. 5 is a perspective view of the impeller, and FIG.
The figure is also a partially opened perspective view of the liner, No. 7
The figure is also a partially cutaway enlarged front view of the impeller, No. 8
The figure is a sectional view taken along the - line in FIG. 7.

In the figure, 1 is a rotating shaft, 2 is a disc-shaped impeller, 3 is an impeller boss, 4 is a hole, 5 is a frame, 6 is a liner, 6A is a recess (Figure 6), and 7 is a valve. , 8 is an elastic body, 9 is a cap, 10 is packing, 11 is a suction port, 12 is a discharge waterway, 13 is a base, 14 is a discharge port, and 15 is a suction waterway.

As shown in FIGS. 5, 7, and 8, 16 is a blade portion consisting of a vortex chamber 26 having a substantially semicircular cross section and blades 27, and 31 is a steam/water separation chamber.

Further, as shown in FIGS. 2, 3, and 4, 17 is a shaft sealing device, 18 is a casing cover, 18A is an end face thereof, 19, 20 is a packing, 21, 22 is a swirl water channel having a substantially semicircular cross section, and 23 is a casing cover. , 24 are the discharge end and suction start end A of the casing cover 18, as shown in FIG. 4, and 25 is the suction start end B of the liner 6, as shown in FIG.

As shown in FIG. 8, 28 is the annular projection 29 at the bottom of the hole, and 30 and 30A are the annular grooves (second
), 32 is a vortex chamber discharge port, and 33 is a rotating shaft mounting hole (FIG. 5).

That is, the rotating shaft 1 of an electric motor etc.
As shown in the figure, the frame 5 is inserted through the packing 19.
The shaft sealing device 17 passes through the liner 6 fitted to the
An impeller 2 is fitted to one end of the rotating shaft 1 so as to be slidable in the axial direction.

In addition, the casing cover 18 is
0 is watertightly fixed to a frame body 5 with bolts (not shown), and this frame body 5 has a suction port 11 connected to a suction pipe, and a check valve is connected by a valve 7 and an elastic body 8. A cap 9 which also serves as a guide for the valve 7 and is screwed in a watertight manner by a packing 10 is provided.
By removing the opening, the opening communicates with the steam/water separation chamber 31 and the suction waterway 15.

In the upper part of the above-mentioned steam/water separation chamber 31, a discharge waterway 1 is provided.
2 is open and communicates with a discharge port 14 connected to a discharge pipe, and the opening of the discharge waterway 12 in the air-water separation chamber 31 is above the suction waterway 15 that opens when the cap 9 is removed. It is formed above the end portion.

Therefore, the pump device as described above is placed on the base 13.

The aforementioned impeller 2 is formed of synthetic resin into a disk shape, and has blades 16 of the same shape on its front and rear surfaces, as shown in FIG. In addition, an impeller boss 3 is formed on this impeller 2 so that the distance between both ends of the impeller boss 3 and the front and rear surfaces of the impeller 2 is the same, and the impeller A hole 4 as shown in FIG. 8 is formed in the boss 3, a part of which is open in the axial direction.

This hole 4 constitutes a hole bottom 29 to the impeller boss 3, and is formed into a pair of holes 4 that are symmetrical to the center of the rotating shaft 1. It is established from
In the case shown in FIGS. 1 and 7, there are two pairs of holes 4 from the front and rear sides.

Further, the blade portion 16 is composed of a vortex chamber 26 and blades 27 related to an impeller, and the cross-sectional shape of the vortex chamber 26 is approximately semicircular as shown in FIG. Whirlpool water channel 2 provided in opposing casing cover 18 and liner 6
1 and 22 are also approximately semicircular in cross section to form a smooth flow of pumped liquid.

The impeller 2 is fitted onto the rotating shaft 1 using a non-circular rotating shaft mounting hole 33.

Although the liner 6 is fitted into the frame body 5, it may be press-fitted or may be slidable in the axial direction.

This liner 6 forms a swirl water channel 22 at a position facing the blade portion 16 of the impeller 2,
An annular groove 30A is formed on the inner circumference of the whirlpool water channel 2.
2, a vortex chamber suction start end B25 connected to the suction waterway 15 of the frame 5 with zero or a small gap, and a vortex chamber discharge port 32 connected to the inside of the steam/water separation chamber 31 are formed.

Further, as shown in FIG. 6, the liner 6 has an end surface in contact with the casing cover 18 on its outer periphery, and a recess 6A that is slightly deeper than the thickness of the impeller 2 on its inner periphery.

The depth of this recessed portion 6A is such that in addition to the thickness of the impeller 2, the depth is increased by a minute gap.

The casing cover 18 is fixed after pressing the liner 6 with its end face 18A, as shown in FIG.

In addition, this casing cover 18 has the same fourth
As shown in the figure, a swirl water channel 21 is formed at a position facing the blade portion 16 of the impeller 2, and an annular groove 30 is formed on the inner periphery of the swirl water channel 21. The portion 23 is formed so as to be symmetrical with the swirl water channel 22 of the liner 6 on both sides of the impeller 2.

Next, the operation of the above-described structure will be explained with reference to FIG. 9, which is a schematic cross-sectional view of the discharge end of the swirl water channel. In FIG. 9, 34 is a bubble.

That is, in the configuration described above, by removing the cap 9, priming the pump, and rotating the rotary shaft 1, the impeller 2 sucks air in the suction pipe.

The air-water mixture discharged by this impeller 2 is
The gas is separated in the steam separation chamber 31, and only the gas is discharged from the discharge channel 12 and the discharge port 14.

By repeating this process, pumping of the liquid is started.

In the liquid lifting operation, the liquid in the vane portion 16 is given energy by rotation, and receives the liquid in the vortex channels 21 and 22 from the inner peripheral side of the vortex chamber 26 having a semicircular cross section. This circular streamline motion, together with the rotational motion of the impeller 2, makes it possible to pump water (liquid) efficiently.

Here, during self-priming operation, the above-mentioned swirl water channel 2
1 and 22, an air-water mixture is generated in which the air in the suction pipe and the priming water are mixed.

However, when the vortex channels 21 and 22 have semicircular cross-sections, the air bubbles 34 move inward in the vortex channel 21, as shown in FIG. The water that does not contain much air bubbles 34 flows to the outside, and at the discharge end portion 23, the water that has flowed to the outside is discharged preferentially into the air-water separation chamber 31. It has been confirmed through experiments that most of the bubbles 34 remain in the vortex chamber 26 of the impeller 2 and return to the suction starting end A24 of the vortex water channels 21, 22.

The bubbles 34, which had been compressed to a small size at the discharge end 23 on the high pressure side of the vortex chamber 26, expand significantly at the suction start end A24 on the low pressure side according to Boyle's law, and fill the vortex waterway 21. do.

During self-priming operation, this phenomenon is repeated, so
It is difficult to obtain high suction power, and it takes a long time to pump water.

In addition, particularly in high suction conditions, cavitation is likely to occur in the low-pressure part of the suction start end A24, and the air bubbles generated at this time remain in the swirl water channel 21 as described above, resulting in a significant decrease in water absorption performance. There were some problems, and it still cannot be called perfect.

In view of the above points, the present invention provides a vortex flow pump having the features described above.

Next, embodiments according to the present invention will be described with reference to FIGS. 10 to 14.

Here, FIGS. 10 and 11 are explanatory diagrams of the cross-sectional area of the swirl water channel according to an embodiment of the present invention, FIG. 12 is a schematic cross-sectional view of the discharge end portion of the swirl water channel, and FIG. , 14 is a performance comparison curve diagram between the one according to the present invention and the already developed product.

In the figures, parts with the same symbols as those in the previous figures 1 to 8 indicate equivalent parts, 34 is a bubble, 35
is the center of the waterway, 36 is the cross-sectional area of the outer waterway, 37 is the cross-sectional area of the inner waterway, 38 is the outer corner, and 39 is the inner corner. teeth,
The performance curve of the embodiment of the present invention, and the broken line B is the performance curve of the already developed product.
This shows a comparison when the same amounts of water and air are introduced.

That is, in the present invention, the first
As shown in Figures 0 and 11, the curvature of the outer corner 38 is larger than the curvature of the inner corner 39 on the discharge side of the swirl water channel 21 in the previous configuration, so that the outer The waterway cross-sectional area 36 on the inner side is formed smaller than the waterway cross-sectional area 37 on the inner side, and the same is true for the vortex waterway 22 on the liner 6 side.

In this embodiment, as shown in FIG. 10, the curvature R (O ₁ center) of the outer corner 38 of the swirl water channel 21 is
By forming the curvature r (O ₂ center) of the inner corner 39 to be larger than that, as described above, the outer side,
The inner waterway cross-sectional areas 36 and 37 are made different.

With this configuration, the vortex chamber 26 of the impeller 2
The water discharged from the vortex channels 21 and 22 to the outer corners 38 is forcibly rotated toward the inner corners 39.

Therefore, as shown in FIG.
Further, the air bubbles are smoothly discharged toward the air/water separation chamber 31 together with the discharged water.

In other words, in the previously developed system described above, water is short-circuited and discharged due to centrifugal force, and air bubbles remain inside, whereas the system according to this embodiment Although the centrifugal force is the same, the water being guided is guided by the large curved side surface on the outside and rotated toward the inside bottom.
As a result, the rotational flow of water becomes a large rotation that reaches the bottom, thereby promoting the discharge of accumulated air bubbles.

Further, by partially changing the cross-sectional area on the discharge side of the swirl water channels 21 and 22, an air discharge effect can be expected without particularly impairing water pumping performance and self-priming performance.

According to these, the amount of air bubbles returning to the suction side is drastically reduced, and as shown in Fig. 13, which shows the change over time in the degree of vacuum reached during self-priming operation, the already developed configuration described in Fig. 9 is shown by the broken line B. Compared to this, in the case of this embodiment shown by the solid line A, a high degree of vacuum can be obtained in a short time.
As a result, the time required for water absorption is significantly shortened.

In addition, regarding the pumping performance in a high suction state, the cavitation phenomenon shown by the solid line A is suppressed compared to the structure shown in FIG. 9, shown by the broken line B in FIG. It has improved pumping performance.

In the above embodiment, both of the swirl water channels 21 and 22 have the above-mentioned cross-sectional shape, but only one of them may have the above-mentioned cross-sectional shape. Including the above-mentioned points, when the present invention is used, the amount of bubbles returning to the suction side is drastically reduced, a high degree of vacuum can be obtained in a short time, and as a result, the time required for water absorption is significantly shortened. In addition, since the cavitation phenomenon is suppressed, water pumping performance can be improved, and by combining these factors, it is possible to provide a vortex flow pump that can obtain stable water suction performance, making it practical. It can be said that this is an excellent invention that can be expected to have remarkable effects.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal cross-sectional view of the previously developed swirl pump, FIG. 2 is a cross-sectional view taken along the - line in FIG. 1, and FIG. 3 is a cross-sectional view taken along the same line. Figure 4 is a perspective view of the casing cover;
FIG. 5 is a perspective view of the impeller, FIG. 6 is a perspective view of the liner partially opened, and FIG. 7 is a perspective view of the impeller.
Similarly, Fig. 8 is a partially cutaway enlarged front view of the impeller.
7 is a cross-sectional view taken along the - line; FIG. 9 is a schematic cross-sectional view of the discharge end of the swirl water channel; FIG. 10;
FIG. 11 is an explanatory diagram of the cross-sectional area of the whirlpool waterway according to an embodiment of the present invention, FIG. 12 is a schematic cross-sectional view of the discharge end of the whirlpool waterway,
FIG. 4 is a performance comparison curve diagram between the product according to the present invention and the previously developed product. 2... Impeller, 6... Liner, 16... Vane part, 18... Casing cover, 21, 22...
Whirlpool waterway, 26... Vortex chamber, 27... Vane, 35...
...Waterway center, 36...Outer waterway cross-sectional area, 37
...Inner waterway cross-sectional area, 38...Outer corner,
39...Inner corner.

Claims (1)

[Claims] 1. A disc-shaped impeller having a plurality of vortex chambers each having a substantially semicircular cross section and a blade section formed of blades on the side surface;
In a whirlpool pump comprising a whirlpool waterway with a substantially semicircular cross section provided opposite to the vane part, the curvature of the outer corner of the whirlpool waterway is partially turned inward on the discharge side of the whirlpool waterway. A vortex flow type pump characterized in that the curvature of the side corner is larger than that of the curvature, and the cross-sectional area of the outer water channel is smaller than the cross-sectional area of the inner water channel.