CN112145409B

CN112145409B - Non-uniform incoming flow suppression device for wing plate at pump inlet

Info

Publication number: CN112145409B
Application number: CN202010886022.8A
Authority: CN
Inventors: 龙云; 强壮; 朱荣生
Original assignee: Jiangsu University
Current assignee: Jiangsu University
Priority date: 2020-08-28
Filing date: 2020-08-28
Publication date: 2022-04-26
Anticipated expiration: 2040-08-28
Also published as: CN112145409A

Abstract

The invention provides a non-uniform inflow suppression device for a wing plate at a pump inlet, belongs to the field of fluid systems, and particularly provides two schemes of a double-wing-plate suppression device and a single-wing-plate suppression device. The double-wing plate restraining device is of an ellipsoidal structure, an ellipsoidal cavity is arranged in the double-wing plate restraining device, the cavity is provided with an inlet end and an outlet end, wing plates which are arranged in a mirror image mode are arranged in the cavity, the wing plates are of an arc-shaped structure, the thickness of the wing plates is gradually increased from the inlet end to the outlet end, and the mirror image axes of the two wing plates have a certain offset from a central axis; the single-wing plate restraining device is provided with only one wing plate in the cavity, the wing plates are arranged in a biased mode, and the other parts are the same as those of the double-wing plate restraining device. When the inhibition device is used, the inhibition device is arranged at the front end of the water inlet of the pump, and after water flow with uneven flow velocity in the pipeline flows through the inhibition device, the flow velocity difference of the water flow in the high-speed area and the low-speed area is reduced, so that the flow velocity of the water flow is stable, and the efficiency and the stability of the operation of the pump are facilitated.

Description

Non-uniform incoming flow suppression device for wing plate at pump inlet

Technical Field

The invention belongs to the field of fluid systems, and particularly relates to a non-uniform incoming flow suppression device at a pump inlet.

Background

Pumps are widely used mechanical devices, and are almost used for conveying liquid, especially in the field of industrial production. Due to factors such as the working environment of the pump, the loop structure and the like, incoming flow at the inlet of the pump is non-uniform, for example, in nuclear power plant equipment, due to the special structure of the lower chamber, incoming flow of the nuclear main pump is non-uniform in flow velocity distribution. The non-uniform inflow adversely affects the efficiency of the pump operation and the stability of the operation, and therefore, it is necessary to develop a suppression device capable of suppressing the non-uniform inflow so as to make the flow rate smooth.

Disclosure of Invention

Aiming at the defects in the prior art, the invention provides a non-uniform inflow restraining device for a wing plate at a pump inlet, which reduces the non-uniform inflow of the pump inlet and stabilizes the flow speed.

The present invention achieves the above-described object by the following technical means.

A pump inlet wing plate non-uniform inflow suppression device comprises an ellipsoidal cavity, wherein the cavity is provided with an inlet end and an outlet end, and a high-speed area wing plate is fixed in the cavity;

the plate thickness of the wing plate in the high-speed area is gradually increased from the inlet end to the outlet end, the upper plate surface and the lower plate surface of the wing plate in the high-speed area are both cambered surfaces, and the concave-convex directions of the two cambered surfaces are consistent with the concave-convex direction of the inner wall of the cavity where the wing plate in the high-speed area is located;

an eccentric shaft is also arranged in the cavity, the eccentric shaft is a virtual axis, the eccentric shaft is parallel to the central shaft of the cavity, and the distance between the eccentric shaft and the central shaft is delta.

Furthermore, the cross-sectional profile of the wing plate in the high-speed area is formed by closing an inlet end circular arc, an outlet end circular arc, an outer profile curve and an inner profile curve, and the outer profile curve and the inner profile curve are tangent to the inlet end circular arc and the outlet end circular arc respectively.

Further, the high-speed region wing plate section shape determining process is as follows: the bone line in the middle of the cross-sectional profile is an arc with the radius of R and the arc length of Ln, and is formed by connecting the circle center P0 of the arc at the inlet end with the circle center Pn of the arc at the outlet end; the length of any point Px on the skeleton from the normal line of the outer contour curve and the inner contour curve is Rx, the arc length of the Px from the P0 is Lx, Rx is R0+ a Lx, a is (Rn-R0)/Ln, 0.025D < R0 < 0.030D, 0.130D < Rn < 0.140D, and D is the inner diameter of the pipeline.

Further, the distance delta between the eccentric shaft and the central shaft satisfies 0.07D < delta < 0.08D.

Further, the process of determining the installation position of the wing plate in the high speed region comprises the following steps:

the length of the middle point Pm of the skeleton line from the eccentric shaft is Hm, and the lengths of the middle point Pm from the inlet end and the outlet end are equal; and the arc length Ln and radius R of the bone line satisfy, Ln ═ pi R (β 0+ β n)/180 °, R ═ Hn-H0)/(cos β n-cos β 0); wherein beta 0 is an incident angle formed by P0 along the tangent line of the bone line and the eccentric shaft, beta n is an emergent angle formed by Pn along the tangent line of the bone line and the eccentric shaft, H0 is the length of P0 from the eccentric shaft, Hn is the length of Pn from the eccentric shaft, and beta 0 is more than 15 degrees and less than 25 degrees, and beta n is more than 22 degrees and less than 27 degrees.

Furthermore, the values of Hm, H0 and Hn satisfy that Hm is 0, -0.13D < H0 < -0.09D and-0.18D < Hn < -0.12D.

In the scheme, the values of Hm, H0 and Hn can also satisfy 0.55D < Hm < 0.65D, 0.46D < H0 < 0.56D, and 0.4D < Hn < 0.5D.

Furthermore, the device also comprises a low-speed area wing plate (14), wherein the upper plate surface and the lower plate surface of the low-speed area wing plate (14) are cambered surfaces, and the concave-convex directions of the two cambered surfaces are consistent with the concave-convex direction of the inner wall of the cavity (10) where the low-speed area wing plate (14) is located.

Furthermore, the low-speed area wing plates (14) and the high-speed area wing plates (13) are arranged in a mirror image mode relative to the eccentric shaft (16), and the high-speed area wing plates (13) are located on the side closer to the inner wall of the cavity (10).

When the device is used, the restraining device is arranged at the front end of the inlet of the pump, the inlet end of the chamber of the restraining device faces the water flow direction, and the outlet end of the chamber of the restraining device faces the pump. Adjusting the installation angle of the inhibition device to enable the wing plates in the high-speed area in the cavity of the double-wing-plate inhibition device to be positioned on the side with higher flow velocity of water flow in the pipeline and the wing plates in the low-speed area to be positioned on the side with lower flow velocity of water flow in the pipeline; or the wing plate in the high-speed area in the chamber of the single wing plate restraining device is deviated to the side with higher water flow speed in the pipeline.

The invention has the beneficial effects that:

(1) the suppression device is arranged at the front end of the pump inlet, so that the flow speed difference between the water flow with higher flow speed and the water flow with lower flow speed in the pipeline can be effectively reduced, the aim of suppressing non-uniform incoming flow is fulfilled, and the working efficiency and the working stability of the pump are improved finally.

(2) The suppression device only comprises the cavity and the double-wing plate or the single-wing plate, achieves the effect of suppressing non-uniform incoming flow by a simple structure, and has small occupied space and wide application range.

(3) The shape and installation position of the wing plate directly determine the suppression effect of the non-uniform inflow, but the suppression effect is in inverse proportion to the mechanical energy loss of the water flow, for example, the thicker the wing plate is, the stronger the suppression effect is, but the loss of the mechanical energy of the fluid is also increased, and the work load of the pump is increased. The invention provides two schemes of a double-wing-plate restraining device and a single-wing-plate restraining device, wherein the double-wing-plate restraining device sets parameters of the shape and the installation position of a wing plate in a high-speed area as follows: r0 is more than 0.025D and less than 0.030D, Rn is more than 0.130D and less than 0.140D, H0 is more than 0.46D and less than 0.56D, Hn is more than 0.4D and less than 0.5D, Hm is more than 0.55D and less than 0.65D, beta 0 is more than 15 degrees and less than 25 degrees, beta n is more than 22 degrees and less than 27 degrees; the single wing plate restraining device sets parameters of the shape and the installation position of the wing plate in the high-speed area as follows: 0.025D < R0 < 0.030D, 0.130D < Rn < 0.140D, -0.13D < H0 < 0.09D, -0.18D < Hn < 0.12D, Hm is 0, 15 degrees < beta 0 < 25 degrees, 22 degrees < beta n < 27 degrees, and provides more balanced values of wing plate shape and installation position, thereby ensuring better suppression effect of non-uniform incoming flow and avoiding overlarge mechanical energy loss of water flow.

Drawings

FIG. 1 is a view showing a double wing restraining device according to the present invention in use;

FIG. 2 is a schematic view of a dual panel restraint apparatus of the present invention;

FIG. 3 is a cross-sectional profile of a wing in the high velocity zone of the present invention;

FIG. 4 is an axial cross-sectional view of the dual panel inhibitor of the present invention;

FIG. 5 is a view showing the relationship between the arc length of the bone line and the eccentric shaft according to the present invention;

FIG. 6 is a diagram showing the relationship between the radius of the bone line and the eccentric axis of the double wing plate restraining device according to the present invention;

FIG. 7 is a view showing a state of use of the single-wing panel restraining device of the present invention;

FIG. 8 is a view showing the structure of the single wing restraining device of the present invention;

FIG. 9 is a graph of the profile radius of the single wing plate inhibitor of the present invention in relation to the eccentric axis;

fig. 10(a) is a diagram showing an incoming flow velocity in the pump inlet pipe when the suppressing device is not provided, (b) is a diagram showing an incoming flow velocity in the pump inlet pipe after being suppressed by the double fin suppressing device, and (c) is a diagram showing an incoming flow velocity in the pump inlet pipe after being suppressed by the single fin suppressing device;

reference numerals: 1. the device comprises a suppression device, 10 chambers, 11 inlet ends, 12 outlet ends, 13 high-speed zone wing plates, 14 low-speed zone wing plates, 15 central shafts, 16 eccentric shafts, 130 bone lines, 131 inlet end circular arcs, 132 outlet end circular arcs, 133 outer contour curves, 134 inner contour curves, 2 pumps and 3 lower chambers.

Detailed Description

Reference will now be made in detail to the embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like reference numerals refer to the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the drawings are illustrative and intended to be illustrative of the invention and are not to be construed as limiting the invention.

Example 1

As shown in fig. 2, the double-wing plate restraining device of the present embodiment is an ellipsoidal structure, and an ellipsoidal chamber 10 is disposed inside the double-wing plate restraining device, and the chamber 10 is provided with an inlet end 11 and an outlet end 12; a high-speed area wing plate 13 and a low-speed area wing plate 14 are arranged in the cavity 10, the high-speed area wing plate 13 and the low-speed area wing plate 14 are arranged in a mirror image mode, the high-speed area wing plate 13 is closer to the inner wall of the cavity 10 relative to the low-speed area wing plate 14, two sides of the high-speed area wing plate 13 and two sides of the low-speed area wing plate 14 are fixed on the inner wall of the cavity 10 through welding, and the outer arc surface of the high-speed area wing plate 13 and the outer arc surface of the low-speed area wing plate 14 are the same as the inner wall arc surface of the cavity 10;

as shown in the cross section of the axis of the damping device in fig. 4, the eccentric shaft 16 is parallel to the central shaft 15 and is spaced by a distance δ; the cross section of the wing plate 13 in the high-speed area and the cross section of the wing plate 14 in the low-speed area are in a mirror image relation by an eccentric shaft 16; the distance δ satisfies: delta is more than 0.07D and less than 0.08D, and D is the inner diameter of the pipeline.

The high velocity zone strakes 13 cross-sectional shape is determined as follows:

as shown in fig. 3, the cross-sectional profile of the wing plate 13 in the freeway area is formed by closing an inlet end circular arc 131, an outlet end circular arc 132, an outer profile curve 133 and an inner profile curve 134, wherein the outer profile curve 133 and the inner profile curve 134 are respectively tangent to the inlet end circular arc 131 and the outlet end circular arc 132, a bone line 130 in the middle of the profile is formed by connecting a circle center P0 of the inlet end circular arc 131 to a circle center Pn of the outlet end circular arc 132, and the bone line 130 is a circular arc with a radius R and an arc length Ln; inlet arc 131 has a radius R0, outlet arc 132 has a radius Rn, and the arc length of any point Px on bone line 130 from P0 is Lx, then the length of the normal from outer profile curve 133 and inner profile curve 134 at point Px is Rx, and:

Rx＝R0+a*Lx (1)

r0 is 0.025D < R0 < 0.030D, Rn is 0.130D < Rn < 0.140D, and a is a constant;

and according to (1) obtaining:

Rn＝R0+a*Ln (2)

further deducing:

a＝(Rn-R0)/Ln (3)

the cross-sectional shape of the high-speed range wing plate 13 can be determined by setting the values of R0, Rn, R and Ln.

The mounting position of the wing plate 13 in the high-speed region is determined by the following parameters:

as shown in FIG. 4, the length of the midpoint Pm of the bone line 130 of the cross section of the wing plate 13 in the high speed region from the eccentric shaft 16 is Hm, and Hm satisfies 0.55D < Hm < 0.65D; the point Pm is equidistant from the inlet end 11 and the outlet end 12; the point P0 is located at one side of the inlet end 11, and the incident angle beta 0 formed by the tangent line P0 to the eccentric shaft 16 along the bone line 130 satisfies 15 DEG < beta 0 < 25 DEG; the point Pn is located on the side of the outlet end 12 and the exit angle betan of Pn with the eccentric axis 16 along the tangent of the bone line 130 satisfies 22 DEG < betan < 27 deg.

As shown in fig. 5, the arc length Ln and its central angle α, radius R, β 0, β n are related as follows:

αn＝90°-βn (4)

α0＝90°-β0 (5)

α＝180°-αn-α0 (6)

bringing (4) and (5) into (6) yields:

α＝β0+βn (7)

obtained according to the formula Ln ═ R ═ pi · α/180 ° of the arc length:

Ln＝πR(β0+βn)/180° (8)

as shown in fig. 6, as in fig. 5, the center of the arc passing through the bone line 130 is taken as the parallel line of the eccentric shaft 16, the distance between the parallel line and the eccentric shaft is x, the length of the point Pn from the eccentric shaft 16 is Hn, Hn satisfies 0.4D < Hn < 0.5D, the length of the point P0 from the eccentric shaft 16 is H0, and H0 satisfies 0.46D < H0 < 0.56D; then Pn is a length Hn + x from the parallel line and P0 is a length H0+ x from the parallel line; the radius R of the arc of the bone line 130 is related to Hn, H0, β n, β 0 as follows:

Hn+x＝R*sin(90°-βn) (9)

H0+x＝R*sin(90°-β0) (10)

the following can be obtained by (9) and (10):

R＝(Hn-H0)/(cosβn-cosβ0) (11)

in summary, the shape and mounting position of the wing 13 in the high-speed region are determined by the parameters R0, Rn, H0, Hn, Hm, β 0, β n, wherein 0.025D < R0 < 0.030D, 0.130D < Rn < 0.140D, 0.46D < H0 < 0.56D, 0.4D < Hn < 0.5D, 0.55D < Hm < 0.65D, 15 ° < β 0 < 25 °, 22 ° < β n < 27 °.

The restraining device is arranged at the front end of the water inlet of the pump 2 when in use.

As shown in fig. 1, the left side is a pump 2, the right side is a nuclear power station lower chamber 3, water in the lower chamber 3 is pumped out by the pump 2 through a water pipe, and due to the special structure of the lower chamber 3, the flow velocity of water flow in the upper layer of the illustrated water pipe is higher than that in the lower layer, that is, the upper layer of the water pipe is a high-speed water flow region, and the lower layer is a low-speed water flow region; the double-wing plate restraining device of embodiment 1 is arranged between a pump 2 and a lower chamber 3, the inner diameters of an inlet end 11 and an outlet end 12 of the restraining device are equal to the inner diameter D of a pipeline, the inlet end 11 is communicated with a water outlet of the lower chamber 3 through a pipeline, the outlet end 12 is communicated with a water inlet of the pump 2 through a pipeline, a wing plate 13 in a high-speed area of water flow is arranged in a high-speed area of water flow, and a wing plate 14 in a low-speed area of water flow is arranged in a low-speed area of water flow.

Example 2

On the basis of the embodiment 1, the low-speed range wing plate 14 is eliminated, namely the restraining device in the embodiment is a single wing plate; the installation position of the high-speed wing plate 13 is adjusted as follows:

as shown in fig. 8, a midpoint Pm of a bone line 130 of the cross section of the wing plate 13 in the high speed region coincides with the eccentric shaft 16, i.e., Hm is 0; the other parameters are unchanged.

As shown in fig. 9, as in fig. 5, the center of the arc passing through the bone line 130 is taken as the parallel line of the eccentric shaft 16, the distance between the parallel line and the eccentric shaft is x, the length of the point Pn from the eccentric shaft 16 is Hn, Hn satisfies 0.12D < Hn < 0.18D, the length of the point P0 from the eccentric shaft 16 is H0, and H0 satisfies 0.09D < H0 < 0.13D; then Pn is x-Hn from the parallel line and P0 is x-H0 from the parallel line; the radius R of the arc of the bone line 130 is related to Hn, H0, β n, β 0 as follows:

x-Hn＝R*sin(90°-βn) (12)

x-H0＝R*sin(90°-β0) (13)

from (12) and (13), the following can be obtained:

R＝(H0-Hn)/(cosβn-cosβ0) (14)

let H0 and Hn take negative values, and take positive values when H0 and Hn shown in FIG. 6 are located above the eccentric shaft 16; h0 and Hn in FIG. 9 take on negative values when they are located below the eccentric shaft 16; then (14) can be modified to (11), i.e.:

R＝(Hn-H0)/(cosβn-cosβ0) (11)

wherein, -0.13D < H0 < -0.09D, -0.18D < Hn < -0.12D;

example 2 the shape of the high-speed range paddle 13 was the same as in example 1, and the position of the eccentric shaft 16 was the same as in example 1.

In summary, the shape and mounting position of the wing 13 in the high-speed region are determined by the parameters R0, Rn, H0, Hn, Hm, β 0, β n, wherein 0.025D < R0 < 0.030D, 0.130D < Rn < 0.140D, -0.13D < H0 < -0.09D, -0.18D < Hn < -0.12D, Hm-0, 15 ° < β 0 < 25 °, 22 ° < β n < 27 °.

Example 2 the containment device housing and internal chamber were the same as in example 1.

As shown in fig. 7, the installation position of the suppression device of the embodiment 2 is the same as that of the embodiment 1, namely, the suppression device is arranged between the pump 2 and the lower chamber 3, the inlet end 11 of the suppression device is communicated with the water outlet of the lower chamber 3 through a pipeline, and the outlet end 12 of the suppression device is communicated with the water inlet of the pump 2 through a pipeline; the high velocity zone fins 13 are offset to the side of the high velocity zone of the water flow.

The suppression effect of the suppression devices of the embodiments 1 and 2 is simulated by ANSYS CFX simulation software, fig. 10(a) shows the incoming flow velocity distribution in the pump water inlet pipeline when the suppression device is not provided, fig. 10(b) shows the incoming flow velocity distribution in the pump water inlet pipeline after the suppression by the double-wing plate suppression device of the embodiment 1, and fig. 10(c) shows the incoming flow velocity distribution in the pump water inlet pipeline after the suppression by the single-wing plate suppression device of the embodiment 2. The darker the color in the figure indicates the lower the flow rate, and by comparing fig. 10(a), fig. 10(b) and fig. 10(c), it can be seen that:

(1) the color of the upper light color area of fig. 10(a) is deepened in fig. 10(b) and fig. 10(c), which illustrate that the water flow rate in the high-speed area is originally slowed down after the water in the pipeline is inhibited by the inhibiting device, and the water flow rate difference between the upper layer area and the lower layer area of the pipeline is reduced, so that the present invention achieves the effect of inhibiting the non-uniform inflow.

(2) In fig. 10(b) and fig. 10(c), the colors of other regions except the upper original high-speed region are not obviously deepened, which indicates that the present invention does not produce a large reduction on the overall flow speed of the water flow in the pipeline, i.e., the present invention has a small effect on the mechanical energy loss of the water flow.

(3) Fig. 10(b) is compared with fig. 10(c), the upper region of fig. 10(b) is darker and more obvious in gradient, the light and dark gradient profile of fig. 10(b) is more regular, and the light and dark gradient profile of fig. 10(c) is more disordered, which illustrates that the suppression effect of the double-wing plate suppression device of the embodiment 1 is better than that of the single-wing plate suppression device of the embodiment 2; however, fig. 10(b) is darker in color than fig. 10(c), and illustrates that the double-vane inhibitor has a higher effect on the mechanical energy loss of the water flow than the single-vane inhibitor.

In conclusion, simulation software verifies that the suppression device can effectively reduce the flow speed difference of water flow in a high flow speed area and a low flow speed area in a pipeline, so that the effect of suppressing non-uniform incoming flow is achieved, the water flow flowing into a pump is stable, no obvious loss is caused to the mechanical energy of the water flow while the suppression effect is achieved, and the operation efficiency and the stability of the pump are improved; the invention provides two technical schemes of a double-wing plate restraining device and a single-wing plate restraining device at the same time, wherein the restraining effect of the double-wing plate restraining device is stronger than that of the single-wing plate restraining device, but the loss of the mechanical energy of water flow is higher than that of the single-wing plate restraining device.

The present invention is not limited to the above-described embodiments, and any obvious improvements, substitutions or modifications can be made by those skilled in the art without departing from the spirit of the present invention.

Claims

1. A pump inlet wing plate non-uniform inflow suppression device is characterized in that: the device comprises an ellipsoidal cavity (10), wherein the cavity (10) is provided with an inlet end (11) and an outlet end (12), and a wing plate (13) in a high-speed area is fixed in the cavity (10);

the thickness of the high-speed area wing plate (13) is gradually increased from the inlet end (11) to the outlet end (12), the upper plate surface and the lower plate surface of the high-speed area wing plate (13) are cambered surfaces, and the concave-convex directions of the two cambered surfaces are consistent with the concave-convex directions of the inner wall of the cavity (10) where the high-speed area wing plate (13) is located; the cross section profile of the wing plate (13) in the high-speed area is formed by closing an inlet end circular arc (131), an outlet end circular arc (132), an outer profile curve (133) and an inner profile curve (134), wherein the outer profile curve (133) and the inner profile curve (134) are respectively tangent to the inlet end circular arc (131) and the outlet end circular arc (132);

the process for determining the cross-sectional shape of the wing plate (13) in the high-speed region comprises the following steps: a bone line (130) in the middle of the cross-sectional profile is an arc with the radius of R and the arc length of Ln, and the bone line (130) is formed by connecting the circle center P0 of the inlet end arc (131) to the circle center Pn of the outlet end arc (132); the length of any point Px on the bone line (130) from the normal lines of the outer contour curve (133) and the inner contour curve (134) is Rx, the arc length of the point Px from the circle center P0 is Lx, Rx = R0+ a x Lx, a = (Rn-R0)/Ln is provided, wherein R0 is the radius of an inlet end circular arc (131), Rn is the radius of an outlet end circular arc (132), 0.025D < R0 < 0.030D, 0.130D < Rn < 0.140D, and D is the inner diameter of the pipeline;

an eccentric shaft (16) is further arranged in the cavity (10), the eccentric shaft (16) is a virtual axis, and the eccentric shaft (16) is parallel to the central shaft (15) of the cavity (10) and has a distance delta.

2. The pump inlet vane non-uniform inflow suppression device of claim 1, wherein: the distance delta between the eccentric shaft (16) and the central shaft (15) meets the requirement that delta is more than 0.07D and less than 0.08D.

3. The pump inlet vane non-uniform inflow suppression device of claim 2, wherein: the installation position of the high-speed area wing plate (13) is determined by the following process:

the length of the middle point Pm of the bone line (130) from the eccentric shaft (16) is Hm, and the length of the middle point Pm from the inlet end (11) to the outlet end (12) is equal; the arc length Ln and the radius R of the bone line (130) satisfy Ln = π R (β 0+ β n)/180 °, R = (Hn-H0)/(cos β n-cos β 0); wherein beta 0 is an incident angle formed by a tangent line of a circle center P0 along a bone line (130) and the eccentric shaft (16), beta n is an emergent angle formed by a tangent line of a circle center Pn along the bone line (130) and the eccentric shaft (16), H0 is the length of the circle center P0 from the eccentric shaft (16), Hn is the length of the circle center Pn from the eccentric shaft (16), and beta 0 is more than 15 degrees and less than 25 degrees, and beta n is more than 22 degrees and less than 27 degrees.

4. The pump inlet vane non-uniform inflow suppression device of claim 3, wherein: the values of Hm, H0 and Hn satisfy Hm =0, -0.13D < H0 < -0.09D, -0.18D < Hn < -0.12D.

5. The pump inlet vane non-uniform inflow suppression device of claim 3, wherein: the values of Hm, H0 and Hn satisfy 0.55D < Hm < 0.65D, 0.46D < H0 < 0.56D, and 0.4D < Hn < 0.5D.

6. The pump inlet wing plate non-uniform inflow suppressing device according to any one of claims 1 to 3 or 5, wherein: the cavity structure is characterized by further comprising low-speed area wing plates (14), wherein the upper plate surface and the lower plate surface of each low-speed area wing plate (14) are cambered surfaces, and the concave-convex directions of the two cambered surfaces are consistent with the concave-convex direction of the inner wall of the cavity (10) where the low-speed area wing plates (14) are located.

7. The pump inlet wing plate non-uniform inflow suppression device according to claim 6, wherein: the low-speed area wing plates (14) and the high-speed area wing plates (13) are arranged in a mirror image mode relative to the eccentric shaft (16), and the high-speed area wing plates (13) are located on one side close to the inner wall of the cavity (10).