A Fibonacci spiral impeller

Abstract

The present invention discloses a Fibonacci spiral impeller, comprising an impeller body, the impeller body comprising a base, blades are arranged on one side of the base, a through hole connected to the output shaft of a motor is opened in the center of the base; the blades are enveloped to form a spatial flow channel, the starting point of the spatial flow channel is arranged on the outside of the through hole, the end point of the spatial flow channel is arranged on the outer edge of the base, the cross section of the spatial flow channel is a groove shape, and the bottom of the spatial flow channel protrudes to the other side away from the blade; the shape of the base is the same as the shape of the outermost 360° frame of the blade; the blade wrap angle is 720° to 1440°, and the trajectory curve of the spatial flow channel is {f(θ, r(θ), H(θ))}. The Fibonacci series impeller of the present invention can reduce the radial force borne by the impeller, improve the head pulsation, and reduce the dynamic load of the shaft system, thereby playing a role in suppressing the vibration of the pump, improving the operating stability of the whole machine, and extending the service life.

Description

Technical Field

[0001] The invention relates to the technical field of centrifugal pump impeller design, in particular to a Fibonacci spiral impeller. Background Art

[0002] The channel impeller is a commonly used impeller structure for sewage pumps. Compared with closed impellers, it has better anti-winding and anti-clogging performance, and has higher wear resistance. At present, the commonly used blade profiles are mainly Archimedean spirals, equivariant angle spirals, logarithmic spirals, involutes and composite profiles. However, when these profile equations are used to solve large blade wrap angles, the blade profiles are prone to S-shape, and the scanning fluid channel is prone to produce wrinkled surfaces. On the one hand, it affects the particle size that can pass through the impeller flow channel, and on the other hand, it causes the placement angle to change non-monotonic, resulting in a large change in the blade load gradient, which in turn causes the fluid to easily escape from the blade. These two factors will lead to reduced passing performance and efficiency of the sewage pump, and will also induce significant vibration and noise in the sewage pump, seriously affecting the operating stability of the sewage pump. Summary of the invention

[0003] The purpose of the present invention is to provide a Fibonacci spiral impeller to solve the problems existing in the above-mentioned prior art.

[0004] To achieve the above-mentioned purpose, the present invention provides the following scheme: The present invention provides a Fibonacci spiral impeller, comprising an impeller body, the impeller body comprising a base, a blade is arranged on one side of the base, a through hole connected to the output shaft of a motor is opened in the center of the base; the blade envelope forms a spatial flow channel, the starting point of the spatial flow channel is arranged on the outside of the through hole, the end point of the spatial flow channel is arranged on the outer edge of the base, the cross-section of the spatial flow channel is a groove shape, and the bottom of the spatial flow channel protrudes to the other side away from the blade; the shape of the base is the same as the shape of the outermost 360° frame of the blade; the blade wrap angle is 720° to 1440°; the trajectory curve of the spatial flow channel is {f(θ, r(θ), H(θ))}, wherein r(θ) is shown in Formula 1, and H(θ) is shown in Formula 2:

[0005]

[0006] In the formula, θ is the variable of the trajectory curve, θ is the polar angle of the curve; r(θ) is the radius function of the trajectory curve; α is the radius function parameter; b is the Fibonacci number; is the maximum polar angle of the trajectory curve; H(θ) is the distance function of the trajectory curve in the axial direction; L is the maximum distance of the trajectory curve in the axial direction; h is the distance function parameter.

[0007] Preferably, the outlet diameter of the impeller is D2, and D2 is as shown in Formula 3:

[0008]

[0009] Where n is the speed; H d is the head under design conditions; Q d is the flow rate under design conditions; ψ d is the head coefficient under design conditions, ψ d As shown in formula 4:

[0010]

[0011] Where n s is the specific speed, n s，Ref =1,n s As shown in formula 5:

[0012]

[0013] Preferably, the outlet width of the impeller is b2, and b2 is as shown in Formula 6:

[0014] b2=k b2 d k ………………………………6

[0015] Where, d k is the maximum particle diameter that the impeller can pass, k b2 is the coefficient, k b2 The value range is 1.05~1.1.

[0016] Preferably, the thickness of the blade (2) is δ, and δ is as shown in Formula 7:

[0017]

[0018] Where u2 is the circumferential velocity at the outlet of the impeller blade (2).

[0019] Preferably, the outlet placement angle of the blade (2) is β2, and β2 is as shown in Formula 8:

[0020]

[0021] Preferably, the maximum polar angle of the trajectory curve As shown in formula 9:

[0022]

[0023] Preferably, the maximum distance of the trajectory curve in the axial direction is L, and L is shown in Formula 10:

[0024] L=D2×(b-1)-2b2×b……………………10

[0025] The present invention discloses the following technical effects: the Fibonacci series impeller of the present invention can reduce the radial force borne by the impeller, improve the head pulsation, and reduce the dynamic load of the shaft system, thereby suppressing the vibration of the pump, improving the operating stability of the whole machine, and extending the service life. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative labor.

[0027] Figure 1 It is a schematic diagram of the traditional impeller structure;

[0028] Figure 2 It is a rear view of the impeller of the present invention;

[0029] Figure 3 This is a schematic diagram of the impeller structure of the present invention;

[0030] Figure 4 This is a front view of the impeller of the present invention;

[0031] Figure 5 is a cross-sectional view of an impeller of the present invention;

[0032] Figure 6 The radial force Lissajous diagram of the conventional impeller and the novel impeller of the present invention is shown;

[0033] Figure 7 The radial force pulsation diagrams of the conventional impeller and the novel impeller of the present invention;

[0034] Figure 8 It is the head pulsation diagram of the traditional impeller and the new impeller of the present invention.

[0035] Among them, 1 is a base, 2 is a blade, 3 is a through hole, and 4 is a spatial flow channel. DETAILED DESCRIPTION

[0036] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0037] In order to make the above-mentioned objects, features and advantages of the present invention more obvious and easy to understand, the present invention is further described in detail below with reference to the accompanying drawings and specific embodiments.

[0038] Reference Figure 1-8 The present invention provides a Fibonacci spiral impeller, comprising an impeller body, the impeller body comprising a base 1, a blade 2 is arranged on one side of the base 1, a through hole 3 connected to the output shaft of a motor is opened in the center of the base 1; the blade 2 is enveloped to form a spatial flow channel 4, the starting point of the spatial flow channel 4 is arranged on the outside of the through hole 3, the end point of the spatial flow channel 4 is arranged on the outer edge of the base 1, the cross section of the spatial flow channel 4 is an arc-shaped groove, the bottom of the spatial flow channel 4 protrudes to the other side away from the blade 2, that is, the arc bottom of the spatial flow channel 4 is arranged on the side of the base 1 away from the blade; the shape of the base 1 is the same as the shape of the outermost 360° frame of the blade 2, that is, the frame of the outermost circle of the blade is the same as the frame of the base; the blade 2 wraps at an angle of 720° to 1440°, and the trajectory curve of the spatial flow channel 4 is a Fibonacci spiral, which is determined by {f(θ, r(θ), H(θ))}, wherein r(θ) is as shown in formula (1), and H(θ) is as shown in formula (2):

[0039]

[0040] In the formula, θ is the variable of the trajectory curve, θ is the polar angle of the curve; r(θ) is the radius function of the trajectory curve; α is the radius function parameter, α=b / 2; b is the Fibonacci number, which is the "golden ratio". is the maximum polar angle of the trajectory curve; H(θ) is the distance function of the trajectory curve in the axial direction; L is the maximum distance of the trajectory curve in the axial direction; h is the distance function parameter, h=2.5lnb.

[0041] The outlet diameter of the impeller is D2, which is shown in Equation 3:

[0042]

[0043] Where n is the speed; H d is the head under design conditions; Q d is the flow rate under design conditions; ψ d is the head coefficient under design conditions, ψ d As shown in formula 4:

[0044]

[0045] Where n s is the specific speed, n s，Ref =1,n s As shown in formula 5:

[0046]

[0047] The outlet width of the impeller is b2, which is shown in Equation 6:

[0048] b2=kb2 d k ………………………………6

[0049] In the formula, k b2 is the coefficient, k b2 The value range of d is 1.05~1.1; k The design of a single-channel impeller depends largely on the maximum particle diameter d that the impeller can pass. k In addition, companies generally use the maximum particle size d k As one of the important parameters for selecting single-channel centrifugal pump products.

[0050] The thickness of blade 2 is δ, which is shown in formula 7. The minimum thickness of blades of multi-blade centrifugal pumps is generally 3mm to 6mm, and the blade inlet is thinner. Sewage pump impellers include single-channel, double-channel and three-channel impellers, but the blade inlet thickness of sewage pump impellers should be thickened to prevent plastics, long fibers and other materials from being attached to the blade inlet edge.

[0051]

[0052] Where u2 is the circumferential velocity at the outlet of impeller blade 2.

[0053] The outlet placement angle of blade 2 is β2, and β2 is shown in equation 8:

[0054]

[0055] Maximum polar angle of trajectory curve As shown in formula 9:

[0056]

[0057] The maximum distance of the trajectory curve in the axial direction is L, which is shown in formula 10:

[0058] L=D2×(b-1)-2b2×b……………………10.

[0059] The radial force Lissajous diagram of the conventional impeller and the new impeller of the present application is shown in Figure 6 As shown, the radial force pulsation is Figure 7As shown in the figure. It can be seen from the Lissajous figure that the radial force distribution of the traditional impeller has large fluctuations, irregularities, and a long deviation from the axis, which leads to large radial vibration displacement of the rotor, increased vibration level of the whole machine, and easy damage to the bearings after long-term operation. However, the new impeller of the present invention adopts bionics technology, so that the impeller bears very small radial force. It can be seen from the figure that the radial force pulsation of the new impeller is very regular and small in value, and the deviation from the axis is close, so that the static load and dynamic load borne by the rotor and bearing are small, which is conducive to suppressing vibration, improving the operating stability of the whole machine, and extending the service life.

[0060] The head pulsation of the conventional impeller and the new impeller of the present application is as follows: Figure 8 As shown. Figure 8 It can be seen that the head pulsation of the traditional impeller is large and changes irregularly, causing the mechanical parts to bear frequently changing dynamic loads and the materials to be easily damaged by fatigue. The head pulsation of the new impeller is small, indicating that the new impeller is subjected to smaller dynamic loads and the impeller-shaft system is relatively stable.

[0061] The Fibonacci series impeller of the present invention can reduce the radial force borne by the impeller, improve the head pulsation, and reduce the dynamic load of the shaft system, thereby playing a role in suppressing the vibration of the pump, improving the operating stability of the whole machine, and extending the service life.

[0062] In the description of the present invention, it should be understood that the terms "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside" and "outside" etc., indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present invention.

[0063] The embodiments described above are only descriptions of the preferred modes of the present invention, and are not intended to limit the scope of the present invention. Without departing from the design spirit of the present invention, various modifications and improvements made to the technical solutions of the present invention by ordinary technicians in this field should all fall within the protection scope determined by the claims of the present invention.

Claims

1. A Fibonacci spiral impeller, characterized in that: The impeller body comprises an impeller main body, the impeller main body comprises a base (1), a blade (2) is arranged on one side of the base (1), a through hole (3) connected to the output shaft of a motor is opened at the center of the base (1); the blade (2) is enveloped to form a spatial flow channel (4), the starting point of the spatial flow channel (4) is arranged outside the through hole (3), and the end point of the spatial flow channel (4) is arranged at the outer edge of the base (1); the cross section of the spatial flow channel (4) is in the shape of a groove, and the bottom of the spatial flow channel (4) protrudes to the other side away from the blade (2); The shape of the base (1) is the same as the shape of the outermost 360° frame of the blade (2); the wrap angle of the blade (2) is 720° to 1440°, and the trajectory curve of the spatial flow channel (4) is {f(θ, r(θ), H(θ))}, wherein r(θ) is as shown in Formula 1, and H(θ) is as shown in Formula 2: In the formula, θ is the variable of the trajectory curve, θ is the polar angle of the curve; r(θ) is the radius function of the trajectory curve; α is the radius function parameter; b is the Fibonacci number; is the maximum polar angle of the trajectory curve; H(θ) is the distance function of the trajectory curve in the axial direction; L is the maximum distance of the trajectory curve in the axial direction; h is the distance function parameter; The outlet diameter of the impeller is D2, which is shown in Equation 3: Where n is the speed; H d is the head under design conditions; Q d is the flow rate under design conditions; ψ d is the head coefficient under design conditions, ψ d As shown in formula 4: Where n s is the specific speed, n s，Ref =1,n s As shown in formula 5: The outlet width of the impeller is b2, which is shown in Equation 6: b2=k b2 d k …………………………………6 Where, d k is the maximum particle diameter that the impeller can pass, k b2 is the coefficient, k b2 The value range of is 1.05~1.1; The thickness of the blade (2) is δ, and δ is shown in Formula 7: Where, u2 is the circumferential velocity at the outlet of the impeller blade (2); The outlet placement angle of the blade (2) is β2, and β2 is shown in Formula 8: The maximum polar angle φ of the trajectory curve is shown in Equation 9: The maximum distance of the trajectory curve in the axial direction is L, which is shown in formula 10: L=D2×(b-1)-2b2×b……………………10.

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