JPS58195093A - Vortex flow type pump - Google Patents

Abstract

PURPOSE:To prevent wearing of a liner surface in a vortex flow type pump due to a foreign material, by providing concaved parts in plural places on one side of an impeller and constituting the concaved parts such that at rotation of the impeller, projected area of the concaved parts in the radial direction to the facing liner surface almost covers said liner surface. CONSTITUTION:Plural concaved parts 12 used for retreating sand are provided to side faces 5A, 5B of an impeller at a face-to-face position to liner surfaces 1A, 2A, when each part 12 at rotation of the impeller is projected on a straight line in the radial direction on the surface 1A, a total length L, the sum of the parts 12 in the radial direction, is formed equal to or above a width l in the radial direction of the surface 1A, and sand entering a fine distance 11 is retreated to the part 12 by rotation of the impeller 5 to prevent wearing of the liner surface of a vortex flow pump.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a whirlpool pump, and more particularly, to a whirlpool pump that prevents deterioration in pumping performance due to sand abrasion.

There are various factors that affect the performance of a vortex pump, but one of the most important factors is the impeller and the liner surface, which is the side surface of the casing or casing cover. There is a problem with small gaps.

This minute gap is 0.05 m in order to prevent the pumped water from flowing back from the discharge side to the suction side and to obtain good pump performance.
It is generally manufactured to maintain a value of approximately m.

However, when this type of pump is used in a newly dug well, especially in the early stages, a large amount of sand is often mixed into the pumped water and sucked up. As the liner surface of the cover wears, the microgap becomes larger than its initial manufacturing dimensions, resulting in a significant drop in performance and contributing to the reduced reliability of conventional vortex pumps. ing.

Regarding this point, repeated experiments and observations by the inventors have revealed the following facts regarding the wear mechanism.

In other words, in the case of conventional vortex flow pumps, there is When sand contained in the pumped water enters, it does not escape even while the impeller is rotating, and concentric wear marks are formed on the liner surface due to the movement of the sand.

Since the rotation continues without the sand being able to escape from the wear marks, the sand expands the wear marks deeper and wider, increasing the gap.

Therefore, since this wear occurs on the entire liner surface as a collection of wear marks caused by a large number of sand, the above-mentioned minute gap is
It was found that the water would inevitably expand, causing a significant decline in its pumping performance.

The present invention is based on the above-mentioned clarification, and is designed to eliminate the drawbacks of the prior art described above.In order to prevent wear caused by sand, it is necessary to remove foreign substances such as sand that have entered minute gaps. This is a vortex flow pump designed to improve reliability by evacuating the air and discharging it quickly within a short period of time to prevent wear on the liner surface and impeller side surface. Its purpose is to provide the following.

A first feature of the vortex flow pump of the present invention is that in the vortex flow pump formed to have a liner surface facing the disc-shaped impeller with a slight gap therebetween, one of the disc-shaped impellers is One or more recesses are provided on the side surface or both sides, and the area projected in the radial direction of the recess onto the opposing liner surface substantially covers the liner surface when the disc-shaped impeller rotates. There is a formed vortex pump.

More specifically, the radial direction of the liner surface of the casing or casing cover regarding the liner surface spans almost the entire width, that is, the area projected in the radial direction onto the opposing liner surface when the disc-shaped impeller rotates covers the liner surface. By providing a recess such as a groove or a hole on the side surface of the disc-shaped impeller so as to almost cover it, the sand interposed on the liner surface is evacuated to the recess while the disc-shaped impeller rotates, and the sand wear marks caused by the sand are removed. This prevents the growth of water and prevents the deterioration of pumping performance.

Further, a second feature of the vortex-type pump of the present invention is that in the vortex-flow pump formed to have a liner surface facing the disc-shaped impeller with a slight gap therebetween, the disc-shaped impeller one or more recesses extending radially outward from the inner edge of the liner surface on one or both of the liner surfaces facing the liner surface; and one or more recesses extending radially inward from the outer edge of the liner surface. The vortex pump has one or more recesses provided independently of each other.

More specifically, the liner surface of the casing or casing cover, which faces the side surface of the disc-shaped impeller through a small gap, has a recess extending radially outward from the inner circumference of the liner surface, and a liner. Each of the recesses extending radially inward from the outer periphery of the surface is provided independently, and the sum of the radial lengths of a pair of independently provided recesses is equivalent to the full radial width of the liner surface. By having the above length, it is possible to evacuate foreign objects such as sand that have entered the minute gap, and prevent wear on the liner surface and the side surface of the disc-shaped impeller.

Next, each embodiment according to the present invention will be described with reference to each figure.

First, FIG. 1 is a cross-sectional side view of essential parts of a swirl pump according to an embodiment of the first aspect of the present invention, and FIG. 2 is a partially opened cross-sectional view taken along line I-I in FIG. Figure 3 is the second
FIG. 2 is an enlarged schematic diagram of the main part of the figure.

In addition, in this embodiment, recesses are formed at multiple locations on both side surfaces of the disc-shaped impeller, and one recess is formed on the liner surface facing each of the recesses.
This relates to a device that has grooves in several places.

In the figure, 1 is the casing, 1A is the liner surface, 1
B is the outer circumference, 1C is the inner circumference, 2 is the casing cover, 2A is the liner surface, 3 is the pump chamber, 4 is the motor shaft, 5 is the impeller related to the disc-shaped impeller, 5A, 5
B shows the side surface of the impeller.

In addition, 6 indicates the suction side, 7 indicates the discharge side, 8 indicates the whirlpool waterway,
9 is a partition, 10 is a gap, 11 is a minute gap, 12 is a recess, 13 is a groove, 14 is a seal box, and 15 is a vortex chamber.

In addition, casing 1. The cane puffer cover 29 impeller S and the like are made of resin or metal made by casting or cutting.

That is, the illustrated swirl type pump has a pump chamber 3 surrounded by a casing 1 and a casing cover 2.
In the vortex water channel 8 from the suction side 6 to the discharge side 7, the rotation of the impeller 5, which is driven by the motor shaft 4 and has a plurality of vortex chambers 15 having a substantially quarter-circular cross section on its side surface, causes In addition to the shape of the impeller 5, factors that affect the pumping performance in this configuration include the outer circumference of the impeller 5. and a partition part 9 separating the suction side 6 and the discharge side 7 of the casing 1.
and a minute gap 11 between the liner surface 1A of the casing 1 and the liner surface 2A of the casing cover 2 facing the impeller side surfaces 5A and 5B.

In particular, regarding the latter minute gap 11, the passage through which water flows backward from the discharge side 7 to the suction side 6 has a pressure difference between the discharge side 7 and the suction side 6, as shown by the broken line arrow in FIG. The size of the minute gap 11, that is, its width, has a very important meaning because it is a relatively large area surrounded by the width portion and the minute gap 11.

In other words, the minute gap 11.1-1 is maintained at a minuscule dimension of about 0.05W+ to suppress backflow from the discharge side 7 to the suction side 6, thereby maintaining good pump performance. be.

As mentioned earlier, according to the inventors' observations, when the minute gap 11 is narrow as described above, among the sand that intervenes there, particularly fine sand with approximately the same diameter as the minute gap 11, the impeller As the wheel rotates 50 times, the impeller side surfaces 5A and 5B of the impeller 5 are worn out while being embedded in the casing 1 or the casing cover 2.

In addition, there have been cases where the liner surface 1A of the casing 1 or the liner surface 2A of the casing cover 2 is worn out while being embedded in the impeller side surface 5A.

As mentioned above, when a large amount of sand is mixed, the impeller sides 5A and 5B wear out in a short time, resulting in a significant drop in water pumping performance.

Therefore, in this embodiment, the liner surface 1A.

By providing a plurality of recesses 12 for sand evacuation on the impeller side surfaces 5A and 5B facing the impeller 2A, sand that has entered the minute gap 11 is evacuated to the recesses 12 by rotation of the impeller 5. This prevents continued wear, and even in the worst case, only minute wear marks from one rotation are produced.

However, in order to maximize this effect, the third
As shown in the figure, when each of the recesses 12 facing the liner surface IA is projected onto the liner surface IA in the radial direction-straight line, the recesses 12 face the liner surface IA.
It is desirable that the total length L, which is the sum of the radial directions, is equal to or greater than, for example, the radial width l of the liner surface 1A, and the same applies to the liner surface 2A. In addition, each recess 12 shown by a chain line in FIG. 3 shows the position when projected onto the liner surface 1A, and the total length L is the length when they are schematically arranged in the radial direction. This is a clear sign.

In other words, each recess 12 when the impeller 5 is rotated.
From the viewpoint of sand evacuation, it is desirable that the projected area of one row in the radial direction covers the liner surfaces 1A and 2A and is 100% or more of the area of that location, but according to experimental results, even about 80%, that is, It has been confirmed that the desired effect can be achieved by just covering the entire surface.

In addition, if a large proportion of the sand evacuated to the four parts 12 mentioned above is mixed with water, the sand will be evacuated to the recess 12 one after another, so that it will eventually be completely filled with sand and will not be effective. It may become.

In the illustrated example, as a countermeasure for such a case, the second,
As shown in Figure 3, casing 1 and casing cover 2
Grooves 13 are provided in the liner surfaces 1A and 2 of the liner surfaces 1A and 2. As a result, the sand that had been evacuated to the recess 12 of the impeller 5 is moved to the grooves 13 of the liner surfaces 1A and 2A by the rotation of the impeller 5. It was confirmed that when the water reaches the vortex 13, the water is discharged from the groove 13 into the vortex waterway 8. Note that if the proportion of sand mixed in is small, this can be omitted.

Therefore, the groove 13 is formed on the liner surface 1A, as shown in FIG.
It is desirable to form the liner so that it does not penetrate from the outer circumference 1B to the inner circumference 1C, and the same applies to the liner surface 2A.

According to this embodiment, the groove 13 is configured as described above.
This is a comparison diagram of performance change curves over time between a conventional product and a conventional product in which the concave portion 12 or a through hole is provided at 9 locations with a hole diameter of 4 mm, as will be described later. As is clear from the experimental results shown in Figure 4 A, at a sand concentration of 300 mg/l, the
The reduction rate of the cut-off total head retention rate when operated for up to 240 hours is significantly different from that of the conventional product shown in FIG. It has been confirmed that there is.

Therefore, the recess 12 can be provided only on one side facing the liner surfaces 1A, 2A, and the number of the recesses 12 can be only one, and the grooves 13 can also be provided in a plurality. The recess 12 can be provided only on one side of the surfaces 1A and 2A, and the recess 12 can be a through hole, as shown by the dotted line in FIG. 1, and in this case it can also be used as a balance hole. It is something that can be done.

Further, the liner surface is provided on the casing and the casing cover, but in the case of connecting the pump, the liner surface is formed between the casings and between the casing and the casing cover.

Next, FIG. 5 is a cross-sectional side view of essential parts of a vortex pump according to an embodiment of the second aspect of the present invention, and FIG. 6 is a partially exploded side view taken along line II-II in FIG. The sectional view, Figure 7, is
FIG. 3 is an enlarged perspective view of the main part of the recessed portion.

In each figure, the same reference numerals as those in the previous figures 1 and 2 indicate equivalent parts, 16 is the impeller related to the disk-shaped impeller, 17 is the casing, 17A is the liner surface, and 17B is the Inner edge, 17C shows outer edge, 18 is casing cover, 18A is liner surface, 18B is inner edge, 18
C indicates an outer edge, 19 is a recess A, 19A is an outer end, and 20 is a recess B.

Therefore, in this embodiment, the liner surface 1 of the casing 17
7A only, two recesses A19 and one recess B20 are provided on the upper and lower sides, but the recess A19
It is sufficient to have only one.

That is, the impeller 16, the casing 7, and the liner surface 17A of the casing cover 18.

The minute gap 11, 11 provided between 18A and 18A is 0.
As in the previous example, the pump performance is kept good by keeping the pumped water to a minute size of about 0.05 mm and preventing pumped water from flowing back from the discharge side 7 to the suction side 6. In the example, the liner surface 17A is provided with two upper and lower recesses A19 extending radially outward from the inner edge 17B of the liner surface 17A so as to communicate with the inside of the seal box 14, and the liner surface 17A On the outer edge 17C side, a recess B20 communicating with the overwater flow path 8 is provided.
It is designed to be installed independently.

Then, the outer end 19A of the recess A19 shown in FIG.
The relationship between the inner circumferential radius r and the outer circumferential radius R of the recess B20 is such that r≧R, and in the radial direction, the dimension l1
They are arranged in such a size that they overlap by the same amount.

That is, the sum of the radial lengths of the pair of upper recesses A19 and B20 is set to be approximately equal to or greater than the full radial width B of the liner surface 17A, so that sand can be sufficiently evacuated. This is what I did.

Note that, as shown in FIG.
One end is connected to the vortex flow channel 8 so that sand that has entered the minute gap 11 is quickly discharged into the vortex water channel 8.

Therefore, even if sand gets mixed into the minute gap 11,
During one rotation of the impeller 16, the sand retreats into the recess A19 or B20, thereby preventing the growth of wear marks on the liner surface 17A.

As a result, wear marks caused by, for example, one grain of sand can be reduced to a minute mark of one rotation or less in the worst case.

Therefore, the above-mentioned recess A19. By providing a plurality of recesses B20 at suitable locations on the liner surface 17A, the abrasion resistance against sand can be improved accordingly.

This is related to what I mentioned earlier, but if the outer radius R of the recess B20 is made shorter and the inner radius r of the recess A19 is made longer, the amount of sand that gets mixed into the seal box 14 will be reduced, and the amount of sand that will be sucked will be reduced. It has been confirmed that sand is easily discharged into the swirl water channel 8 on the side 6 side, and that the amount of performance deterioration tends to be suppressed.

In the above embodiment, each concave portion is provided only on the liner surface 17A of the casing 17.
This means that the casing cover 18 is
Even if A is worn out, the liner surface 17 is different from the casing 17 and can be easily removed for repair or replacement.
It is designed to have a hole on the A side, and of course, the same shape can be provided on both liner surfaces.

In the configuration described above, the recessed portion A19 and the recessed portion B2 of ■
8, which is a comparison diagram of performance change curves over time, based on a comparative experiment between an example in which one piece of 0 is provided on the liner surface of both the casing and the casing cover, and a conventional product that is not provided with four parts. As is clear from the experimental results of this example shown in Figure 9 A, the retention rate of the cut-off total head (cut-off total head after the test / cut-off total head before the test) compared to the conventional product B ), and the retention rate of pumped water (water pumped after the test / pumped water before the test).

Therefore, in this embodiment having the above-mentioned configuration, similarly to the embodiment shown in FIGS. 1 and 2, a recess or a through hole is formed in the impeller as shown by the broken line in FIG. This does not preclude the provision of such information.

Still, in this embodiment, the recess B20 is formed by recessing a part of the liner surface 17A, but this is because the casing 21 having the liner surface 22 Even if the concave portion C24 is formed in such a manner that the vortex waterway 23 is expanded or curved toward the center,
It has been experimentally confirmed that the same effect as the configuration shown in FIG. 7 can be obtained.

Note that the chain line in FIG. 10 indicates the recess B2. in the embodiment of FIG. 5.6. This is shown in comparison with O.

In summary, according to the present invention, even if sand is mixed in the pumped water, it can be evacuated to the recesses provided on the side of the impeller, the casing, the liner surface of the casing cover, etc. This invention suppresses wear on the side surfaces and liner surfaces, prevents early deterioration of pumping performance, and has a remarkable effect on improving the reliability of vortex pumps.It is an invention with excellent practical effects. .

[Brief explanation of the drawing]

FIG. 1 is a cross-sectional side view of essential parts of a swirl pump according to an embodiment of the first invention, FIG. 2 is a partially opened cross-sectional view taken along line I-I in FIG. 1, and FIG. is an enlarged schematic diagram of the main parts of Fig. 2,
Fig. 4 is a comparison diagram of performance change curves over time between the above-mentioned embodiment and a conventional product based on experimental results, and Fig. 5 is a cross-sectional side view of the main part of the vortex pump according to the embodiment of the second invention. 6 is a partially opened cross-sectional view taken along line II-II in FIG. 5,
Fig. 7 is an enlarged perspective view of the main part of the concave portion, Fig. 8.9
The figure is a performance change curve over time of the product according to an embodiment of the second invention and the conventional product, and FIG. 10 is a sectional view of a main part of the product according to another embodiment. 1.17.21...Casing, 2,18...Casing cover, 1A, 2A, 17A, 18A, 22...
・Liner surface, 1B...outer circumference, 1C...inner circumference, 5,
16... Impeller, 5A, 5B... Impeller side direction, 8,
23... Eddy water channel, 11... Minute gap, 12...
Recessed portion, 13...Groove, 17B, 18B...Inner edge, 17
C, 18C...outer edge, 19, 20, 24...recess A
, B, C, 19A...outer edge. 4th rz3, Jx Figure 69 $lO port #l 57

Claims (1)

[Scope of Claims] 1. In a vortex flow pump formed to have a liner surface facing a disc-shaped impeller with a small gap therebetween, one or more places on one or both sides of the disc-shaped impeller are provided. A vortex flow type characterized in that the concave portion is provided at several locations, and the concave portion is formed so that the radial projected area of the concave portion onto the opposing liner surface substantially covers the liner surface when the disc-shaped impeller rotates. pump. 2. In the product described in claim 1, one or both of the liner surfaces facing the disc-shaped impeller are provided with grooves for sand removal at one or more locations. A vortex pump. 3. A vortex flow pump according to claim 1, wherein the recess provided on the side surface of the disc-shaped impeller is a through hole that also serves as a balance hole of the impeller. 4. In the item described in claim 1, the radial projected area of the four parts on the opposing liner surface when the disc-shaped impeller rotates accounts for at least 80% or more of the area of the liner surface. A vortex pump with a recessed part so that 5. In the item described in claim 2, the groove provided in one or both of the liner surfaces facing the disk-shaped impeller is formed so as not to penetrate from the outer periphery to the inner periphery of the liner surface, A vortex flow pump is designed to prevent water leakage that affects pumping performance. 6. In a vortex flow pump formed to have a liner surface facing the disk-shaped impeller with a slight gap, one or both of the liner surfaces facing the disk-shaped impeller have an inner edge of the liner surface. One or more recesses extending radially from the outer edge of the liner surface and one or more other recesses extending radially inward from the outer edge of the liner surface, each independently. A vortex flow pump characterized by being provided with a 7. In the item described in claim 6, the inner edge,
A vortex flow pump, wherein the sum of the radial lengths of a pair of recesses provided independently from the outer edge is greater than the total radial width of the liner surface. 8. A vortex flow pump according to claim 6, wherein a recess provided at the outer edge of the liner surface is formed to communicate with the vortex waterway.