JPS6350688A - Rubber impeller - Google Patents

Abstract

PURPOSE:To prevent a rubber impeller, a front cover and a wear plate from being damaged due to deformation of the blade part during curving, by making the width of the blade part between both side ends thereof on the compression side less than the width thereof between both side ends on the expansion side. CONSTITUTION:A rubber impeller 10 is formed in a cylindrical shape, having its outer surface attached thereto with a plurality of blade parts 2 of a substantially steering wheel-like cross-sectioned shape. During operation of a pump, when a discharge pressure acts upon on the compressing side 17 of the blade part 2, compression deformation occurs due to slidably contact between the blade part 2 and the inner surface of a casing, both side ends of the compression side 17 of the blade part 2 are liable to bulge out. However, since the blade part has curved parts having radius R of curvature in both side end parts so that the width of the compression side 17 between both side ends is less than that of the extension side 18 between both side ends, both side ends of the blade part does not substantially bulges out, thereby it is possible to prevent the blade part 2 itself, a front cover and a wear plate from being damaged.

Description

DETAILED DESCRIPTION OF THE INVENTION (a) Industrial Application Field The present invention relates to a rubber impeller for a pump that sucks in and pushes out liquid by the action of pressure.

(B) Conventional technology In a conventional pump, as shown in a partially cutaway front view in FIG. 6 and a side view in FIG. A pulley 0υ is fixed to the rear end of the rotating shaft (7) and is located at the rear of the housing (6), and an impeller 0φ is fixed to the front end of the rotating shaft (7) and the housing (6) in front of. A casing (5) is fixed to the front end of the housing (6) via a wear plate (8), and a front cover (9) is screwed to the front end of the casing (5).

The impeller αω is in sliding contact with the inner circumferential curved surface of the casing (5), and both end surfaces of the impeller 0ω are in contact with the wear plate (8).
The driving force of the motor (not shown) is transmitted to the impeller aω via the pulley aυ and the rotating shaft (7), and the impeller 00 ) is inside the casing (5) and is rotated. On the outer peripheral surface of the casing (5), an inlet port and a discharge port 0) are formed in a substantially perpendicular direction so as to communicate with the inner space, and the force between the two inlets (2) and the discharge port α is formed. A comb-shaped sleeve having a substantially crescent-shaped cross section is fixed to the inner peripheral surface of the casing so that the distance in the radial direction is reduced.

Since the outer diameter of the impeller 0ω is slightly larger than the inner dimension of the casing (5), the blades α of the impeller QQI remain in a slightly curved shape and the impeller 0ω is fitted into the casing (5). Ru.

Therefore, when the impeller αO) is slid and rotated in the casing (5) from the suction port (2) to the discharge port Q31, the blade 0 of the impeller α0) is always curved by the inner peripheral surface of the casing (5). However, when the blade α4 begins to come into sliding contact with the comb-shaped sleeve αa, the curvature of the blade α4 becomes deeper.

By the way, when using this conventional pump to discharge seawater at a discharge pressure of 6 kg/cflI, for example, 1.5 k
h motor was required. This requires a motor with a higher output than a normal pump, and the reason for this is that even when running idle, a considerably large torque is required. Front cover (9
) and the sliding surfaces of the wear plate (8) with both ends of the blades 0 are well damaged, and in particular the sliding surfaces with both ends of the blades αω in the range that slides into the comb-shaped sleeve α ship are severely damaged.

Therefore, it is often necessary to remove the front cover (9) and replace the impeller, which is time consuming and inconvenient to the user.

In addition, the capacity of the motor is too large for the discharge pressure and discharge amount of seawater, so it is difficult to reduce the weight, and transportation and maintenance costs are high.

As shown in Figure 4, an impeller (
10), especially when its blade α9 is bent from the dotted line position to the solid line position, the front cover (9) and the wear plate (8 ), it was found that the width of the θ mark on the extension side is smaller than H, and the width h2 of the compression side 0η is larger than H. For example, impeller 0ω
Width 11 I=50.5 fl and thickness t'= of blade 09
In case of 5.5mm, compression side 07) = 52°5
~53.0mm extension side aa+, h + =49.7m
m.

(c) Problems to be Solved by the Invention The present invention solves the problem that even when the impeller (QO) formed of rubber is in operation, both end surfaces of the compressed side of the blades 09 of the impeller αω bulge. In the rubber impeller 0ω for a pump with a small amount of friction, the inner surface of the front cover (9) and the wear plate (8) may be damaged by the end surfaces on both sides of the compression side of the blade α9 of the impeller αω during operation of the impeller aω. In addition, since the frictional resistance between the end surfaces of the blades α and both inner surfaces of the front cover (9) and the wear plate (8) can be reduced, the weight of the motor that drives the impeller aω can be reduced. It is an object of the present invention to provide a rubber impeller aω for a pump that can extend the service life of the impeller αω, the front cover (9), and the wear plate (8). In the rubber impeller C1ot for a pump, the impeller C1ot is made of a rubber impeller for a pump consisting of a shaped impeller QO) and a vane part (2) with a substantially steering wheel-shaped cross section attached to the outer surface of the impeller C1ot.
When the blade is compressed and deformed by the inner surface of the casing (5), the rear ends (3) on the compression side of the blade (2) expand outward to approximately the specified width of the impeller. It is characterized by being configured.

(E) Embodiment FIG. 1 is a front view showing an embodiment of the impeller aΦ of the present invention, FIG. 2 is a sectional view taken along line A-A in FIG.
The figure is a sectional view taken along the line B-B in FIG. 1.

The impeller αω is formed from a cylindrical impeller bushing (1) made of metal, and a rubber blade portion (2) coated on the outer surface of the impeller bushing (2) having a substantially steering wheel-shaped cross section. The impeller bush (1) is pivotally supported on the front end of the rotating shaft (7) as shown in FIG. Therefore, the inner surface of the impeller bush (1) is provided with a vertical groove in the direction of the rotation axis, and is fitted with the vertical groove provided at the front end of the rotation shaft (7), thereby removably and reliably controlling the motor torque. is transmitted. The blade part (2) is attached to the outer surface of the impeller bushing (1) to be wider than the width of the impeller bushing (1), and consists of a base part and two radially extending blades,
The width H1 is determined by the width of the front cover (9) fixed to the front and rear end surfaces of the casing (5), as shown in Figure 6.7.
The distance H between the wear play H81 and the wear play H81 is approximately equal to or slightly larger.

In this example, impeller 0010 width HI = 50.5 m
m.

Diameter d 3 of base 0Q of blade part (2) = 4.6 mm,
The outer diameter d4 of the blade portion is 91 mm, and the thickness t of the blade 09 is 5.
5mm, the roundness of both end faces on the compression side of the blade α is radius R = 6
In the case of binding on a curved surface of mm, as shown in FIG. 8, even if the blade α was curved, the width of the compression side αη did not bulge out too much on both end faces, and was almost equal to the width H1 of the impeller.

The radius dimension of the roundness R can be selected within the range of 1 to 1511III+.

The impeller bush (1) selects a metal material suitable for the liquid. As for the material of the vane portion (2), if the liquid is seawater, CR or NBR is suitable, but depending on the type of liquid, synthetic rubber or other material suitable for the liquid may be selected.

In this embodiment, only the compression side a force of the impeller 00 is not applied to both ends, so that the inner surfaces of the front cover (9) and the wear plate (8) are not damaged.

FIGS. 9(a) and 9(b) show a second embodiment of the present invention, and show sectional views similar to FIG. 3 of the blade αω.

(a) Both side end surfaces of the blade α in the figure are on the compression side αη
Both α and extension side α are rounded, and compression side αη
The end face of is formed as a curved surface with radius R" 5 mm, and the end face on the % extension side α0 is formed as a curved surface with radius R-4 mm. Of course, (b)
Even if it is formed into a shape with rounded corners instead of roundness as shown in the figure,
Almost the same effect can be obtained.

The rest of the structure is the same as that of the first embodiment, and the same reference numerals indicate the same parts.

For example, a performance test was conducted using an impeller with an outer diameter of 105a+m of the blade portion (2) and a CR material with a hardness rating of 65 to 66 on a JIS A type hardness tester, and the following results were obtained.

As mentioned above, the static starting torque and rotational resistance of this example are excellent.

In this embodiment, since both end surfaces of the blade part (2) are rounded, there is no bulge or contraction on both end surfaces of the compression side Q7) and the expansion side α (the intermediate part of the compression and expansion Therefore, the contact area between the wear plate (8) and both inner surfaces of the front cover (9) became extremely small, and therefore the frictional resistance became extremely small.

FIG. 10 shows a third embodiment of the present invention.
A cross-sectional view similar to the figure is shown.

The cross section of each blade θ is formed into an isosceles trapezoid shape, and both end surfaces thereof are undercut on the compression side cm.

The rest of the structure is the same as that of the first embodiment. In the case of this embodiment, manufacturing is easy because it is simply canted diagonally.

(f) Effects of the Invention The present invention provides a pump impeller consisting of a cylindrical impeller bush and a vane portion whose cross section is approximately the shape of a steering wheel, which is attached to the outer surface of the impeller bush. At least both ends of the rear surface have been removed so that they are rounded,
When the blade is compressed and deformed by the inner surface of the casing, both ends of the rear surface of the blade are configured so as not to bulge outward too much. The contact pressure during sliding contact with the inner surface is extremely small, eliminating damage to both inner surfaces of the front cover and wear plate, reducing the effort and loss of replacing them, and extending the service life. The reduction in torque made it possible to reduce the weight of the motor, contributing to reductions in running costs, transportation costs, etc.

[Brief explanation of drawings]

FIG. 1 is a front view of the first embodiment of the present invention, and FIG. 2 is a front view of the first embodiment of the present invention.
3 is a sectional view taken along line BB in FIG. 1, FIG. 4 is a side view showing a partially curved state of a conventional blade, and FIG. 6 is a partially cutaway front view of the pump, and FIG. 7 is a side view of FIG. 6.
Figure 8 is a cross-sectional view of the blade in the first embodiment when it is curved, Figures 9a and b are cross-sectional views of the blade in the second embodiment, and Figure 10 is a cross-sectional view of the blade in the third embodiment. FIG. (1) -1-impeller bush, (2) -blade part, (3) -rear end part, (4) -roundness, (5)
・Casing, (6) - Housing, (7) - Rotating shaft, (8) - Wear plate, (9) - Front cover, (10) - Impeller, (11) - Pulley,
(12) - Suction port, (13) - Discharge port, (14) - Comb-shaped sleeve, (15) - Vane, (16) - Base, (17)
- Compression side, (18)-expansion side.

Claims (1)

[Claims] In a rubber impeller for a pump consisting of a cylindrical impeller bushing (1) and a vane part (2) with a substantially steering wheel-shaped cross section attached to the outer surface of the bushing, the vane part (2) is attached to the inner surface of the casing (5). Rubber for a pump configured such that, when compressed and deformed, both ends (3) of the rear surface of the blade (2) on the compression side bulge outward to approximately the specified width of the impeller. Made of impeller.