Impeller for livestock and negative pressure fan with the same

Abstract

The invention relates to a kind of impeller for livestock, and the inner big blade is straight plate type blade near the inner hub side, and is bent and twisted type blade near the outer hub side; the outer blade is bent and twisted type blade near the outer hub side, and is straight plate type blade far from the outer hub side; the inner small blade is geometrically similar to the outer blade in structure; the outer hub between adjacent outer blades is provided with a steady flow hole, and the center line of the steady flow hole is not collinear with the impeller center; the radius of the outer hub is R, the outer radius of the bent and twisted part of the outer blade is R2, and the inner radius of the bent and twisted part of the inner big blade is R1, wherein R2=(1.3-1.5)R, and R1=(0.6-0.9)R. Due to the improvement of the impeller and blade structure, the wind pressure is effectively improved, the noise is reduced, the stability is improved, the surge is reduced, and the efficiency is improved.

Description

Technical Field

[0001] This invention relates to the field of fluid machinery technology, specifically to an impeller for livestock use, and more specifically to a negative pressure fan having the impeller. Background Technology

[0002] Livestock fans are axial flow fans specifically designed for ventilation in livestock farming and industry. They achieve ventilation and cooling through negative pressure air exchange and are widely used in farms, factory workshops, and other similar locations. Existing livestock fans on the market typically suffer from low air pressure, high noise, poor stability, high surge, and low efficiency. As demands for livestock fans increase, the need for efficiency improvements is growing. The design of the impeller and blades directly affects the fan's efficiency; optimizing the impeller and blade layout can significantly improve the aforementioned shortcomings. Therefore, optimizing the design of livestock fans is essential.

[0003] Prior art CN113464471A discloses a livestock ventilation system, including a ventilation duct 1, a fan shaft 2 disposed inside the ventilation duct 1, a fixed shaft 11 connected to the end of the fan shaft 2, and blades 3 disposed on the fixed shaft 11. The blades 3 have a pointed front end, are thicker in the middle and thinner at the tail end, and are shaped like willow leaves. The blades 3 are made of carbon fiber material and have a polytetrafluoroethylene coating. An angle adjustment mechanism 13 is disposed at the connection between the fixed shaft 11 and the blades 3. The fixed shaft 11 is equipped with... A transverse groove 14 is provided, a blade 3 is provided, and a support frame 4 is provided on the wall of the air duct 1. One support frame 4 is provided at the top and one at the bottom of the air duct 1. A support shaft 5 is connected to the support frame 4. An anti-backflow butterfly 6 is installed on the support shaft 5. An installation clip 7 is provided on the anti-backflow butterfly 6. The anti-backflow butterfly 6 is installed on the support shaft 5 through the installation clip 7. A limit clip 8 is connected to the bottom of the support shaft 5. A card seat 9 is connected to the limit clip 8. The card seat 9 is provided on the air duct 1. An installation seat 10 is provided at the end of the air duct 1. The integrated air duct can more effectively prevent rainwater from entering the fan. The butterfly valve of this invention is designed to be installed at an angle and fall with its own weight. The butterfly valve installation part only needs to be fixed with a bending plate and round steel. It opens automatically when the motor is turned on, which greatly reduces assembly time and processing costs, further reducing the cost of the fan product. The fan blades have better rigidity and are not easy to deform. Even when working in this environment, the air volume reduction is not significant. In addition, the material is moisture-proof, corrosion-proof, anti-aging, has a long service life, is lightweight, and saves energy.

[0004] However, the above-mentioned impeller and blade structure has design limitations, involving only the design of some simple impeller and guide vane structures, without fundamentally changing the relevant structure, resulting in problems such as low wind pressure, high noise, poor stability, high surge, and low efficiency. Therefore, in order to address these problems, the applicant proposes an impeller for livestock and a negative pressure fan with such impeller. Summary of the Invention

[0005] The purpose of this invention is to overcome the shortcomings of the prior art by proposing an impeller for livestock and a negative pressure fan having the impeller.

[0006] To achieve the above objectives, the present invention adopts the following technical solution:

[0007] An impeller for livestock use includes an inner hub, inner large blades, inner small blades, an outer hub, and outer blades. The inner large blades and inner small blades are alternately and evenly arranged on the outer ring of the inner hub. The inner ring of the outer hub is fixed to the tip of the inner large blades. The outer blades are evenly arranged on the outer ring of the outer hub. The impeller is characterized by: the inner large blades, inner small blades, and outer blades being composite blades; the inner large blades are straight-plate type near the inner hub and curved / twisted type near the outer hub; the outer blades are curved / twisted type near the outer hub and straight-plate type away from the outer hub; the inner small blades and outer blades are geometrically similar in structure; flow stabilizing holes are provided on the outer hub between adjacent outer blades, and the centerline of the flow stabilizing holes is not collinear with the impeller center; the radius of the outer hub is R, the outer radius of the curved / twisted portion of the outer blades is R2, and the inner radius of the curved / twisted portion of the inner large blades is R1, where R2 = (1.3~1.5)R and R1 = (0.6~0.9)R.

[0008] Furthermore, the angle between the centerline of the flow stabilizing orifice and the radius line at that location is A, where A = 10° to 60°.

[0009] Furthermore, the tip radius of the inner leaflet is R3, where R3 = (0.3~0.6)R.

[0010] Furthermore, the flow stabilizing orifice is located closer to the trailing edge of the outer blade.

[0011] Furthermore, the chord length corresponding to the outer side of the outer blade's twisted portion is L1, and the chord length corresponding to the inner side of the inner blade's twisted portion is L2, where L1 > L2, and L1 = (1.1~1.3)L2.

[0012] Furthermore, the impeller surface is covered with a wear-resistant and corrosion-resistant composite film.

[0013] Furthermore, the composite membrane is made of fiberglass.

[0014] A negative pressure fan, characterized in that the fan includes a guide ring, a motor, a motor bracket and a shaft sealing structure, an impeller is fixed to the end of the motor, the motor is installed inside the guide ring through the motor bracket, and the impeller and the shaft are sealed by a sealing structure, wherein the impeller is the livestock impeller described above.

[0015] Furthermore, the sealing structure is an oil-sealed structure using a sealing ring and an outer cover.

[0016] Furthermore, the motor bracket has a "T" shaped structure.

[0017] Furthermore, the inner wall of the guide ring is provided with a guide structure along the flow path direction, and the cross-sectional curve formed by the radial section of the guide structure after unfolding is a sine curve or a cosine curve.

[0018] Furthermore, the axial length of the impeller is W1, the inlet end of the guide structure coincides with the foremost front end of the radial projection of the impeller on the inner wall of the guide ring, and the axial length of the guide structure is W2, where W2 = (0.3~0.8)W1.

[0019] This invention discloses an impeller for livestock use, comprising an inner hub, inner large blades, inner small blades, an outer hub, and outer blades. The inner large blades and inner small blades are alternately and evenly arranged on the outer ring of the inner hub. The inner ring of the outer hub is fixed to the tip of the inner large blades. The outer blades are evenly arranged on the outer ring of the outer hub. The inner large blades, inner small blades, and outer blades are all composite blades. The inner large blades are straight blades near the inner hub and curved / twisted blades near the outer hub. The outer blades are curved / twisted blades near the outer hub and straight blades away from the outer hub. The inner small blades and outer blades are geometrically similar in structure. Flow stabilizing holes are provided on the outer hub between adjacent outer blades, and the centerline of the flow stabilizing holes is not collinear with the impeller center. The radius of the outer hub is R, the outer radius of the curved / twisted portion of the outer blade is R2, and the inner radius of the curved / twisted portion of the inner large blade is R1, where R2 = (1.3~1.5)R and R1 = (0.6~0.9)R. Improvements to the impeller and blade structure effectively increase wind pressure, reduce noise, enhance stability, reduce surge, and increase efficiency. Attached Figure Description

[0020] Figure 1 This is an exploded view of the structure of the present invention;

[0021] Figure 2 This is an axial structural cross-sectional view of the present invention;

[0022] Figure 3 This is a schematic diagram of the radial cross-section of the flow guiding structure.

[0023] Figure 4 This is a schematic diagram of the impeller structure;

[0024] Figure 5 Schematic diagram of the relative dimensions of the impeller

[0025] In the diagram: Inner hub 1, Inner large blade 2, Inner small blade 3, Outer hub 4, Outer blade 5, Flow stabilizing orifice 6, Flow guide ring 7, Motor 8, Motor bracket 9, Flow guide structure 10, Outer hub 4 radius R, Outer blade 5 outer radius of the bend R2, Inner large blade 2 inner radius of the bend R1, Inner small blade 3 tip radius R3, Angle A formed by the centerline and radius line of the flow stabilizing orifice 6, Chord length L1 corresponding to the outer side of the bend L1 of the outer blade 5, Chord length L2 corresponding to the inner side of the bend L2 of the inner large blade 2, Impeller axial length W1, Flow guide structure 10 axial length W2. Detailed Implementation

[0026] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0027] The present invention will now be described in further detail with reference to the accompanying drawings.

[0028] like Figure 1-5 As shown, a livestock impeller includes an inner hub 1, inner large blades 2, inner small blades 3, an outer hub 4, and outer blades 5. The inner large blades 2 and inner small blades 3 are alternately and evenly arranged on the outer ring of the inner hub 1. The inner ring of the outer hub 4 is fixed to the tip of the inner large blades 2. The outer blades 5 are evenly arranged on the outer ring of the outer hub 4. The impeller is characterized in that: the inner large blades 2, inner small blades 3, and outer blades 5 are all composite blades; the inner large blades 2 adopt a straight blade type near the inner hub 1 and a curved / twisted blade type near the outer hub 4; the outer... The blade 5 is a twisted blade near the outer hub 4, and the outer blade 5 is a straight blade away from the outer hub 4. The inner small blade 3 is geometrically similar to the outer blade 5. A flow stabilizing hole 6 is provided on the outer hub 4 between adjacent outer blades 5. The center line of the flow stabilizing hole 6 is not collinear with the impeller center. The radius of the outer hub 4 is R, the outer radius of the twisted part of the outer blade 5 is R2, and the inner radius of the twisted part of the inner large blade 2 is R1, where R2 = (1.3~1.5)R and R1 = (0.6~0.9)R.

[0029] The design of blade geometry, number, angle, layout, and torsion has a profound impact on the performance, efficiency, lifespan, and operational stability of the impeller. The applicant's research has found that when a livestock fan adopts a double-layer blade structure, the optimized design of its blade layout and structure can significantly solve problems such as low wind pressure, high noise, poor stability, high surge, and low efficiency. However, double-layer blades have inherent defects, namely, unstable or disordered flow patterns on both sides of the outer hub. The blade structure on both sides of the outer hub has a significant effect on changing this situation. Based on this, the applicant has optimized the design and layout of the inner and outer blades. The inner large blade 2, near the inner hub 1, adopts a straight plate blade design. The outer blades 5 and 2 are designed with curved and twisted blades on the side near the outer hub 4 and straight blades on the side away from the outer hub 4. The inner small blades 3 and 2 are geometrically similar in structure. Each outer hub 4 between adjacent outer blades 5 is provided with a flow stabilizing hole 6, the center line of which is not collinear with the impeller center. The radius of the outer hub 4 is R, the outer radius of the curved and twisted part of the outer blade 5 is R2, and the inner radius of the curved and twisted part of the inner large blade 2 is R1, where R2 = (1.3~1.5)R and R1 = (0.6~0.9)R. This design effectively improves wind pressure, reduces noise, enhances stability, reduces surge, and increases efficiency.

[0030] Furthermore, the angle between the centerline of the flow stabilizing orifice 6 and the radius line at that position is A, where A = 10° to 60°.

[0031] Furthermore, the position of the flow stabilizing orifice 6 is closer to the trailing edge of the outer blade 5.

[0032] Considering the significant pressure difference between the inner and outer blades, the applicant found that installing flow stabilizing holes on the outer hub can achieve a good effect of balancing and stabilizing the pressure between the inner and outer blades.

[0033] Furthermore, the tip radius of the inner leaflet 3 is R3, where R3 = (0.3~0.6)R.

[0034] The inner blade 3 and the outer blade 5 are geometrically similar in structure. This structure can better optimize the flow channel on the inner hub side, making the pressurization and conveying effect more obvious.

[0035] Furthermore, the chord length corresponding to the outer side of the twisted portion of the outer blade 5 is L1, and the chord length corresponding to the inner side of the twisted portion of the inner large blade 2 is L2, where L1 > L2 and L1 = (1.1~1.3)L2.

[0036] The chord length design can significantly improve work efficiency, make airflow smoother, and make the fan more energy-efficient.

[0037] Furthermore, the impeller surface is covered with a wear-resistant and corrosion-resistant composite film.

[0038] Furthermore, the composite membrane is made of fiberglass.

[0039] Considering the wear and corrosion issues that wind turbines may experience, the applicant chose to cover the impeller surface with fiberglass material to extend its service life.

[0040] A negative pressure fan, characterized in that the fan includes a guide ring 7, a motor 8, a motor bracket 9, and a shaft sealing structure, an impeller is fixed to the end of the motor 8, the motor 8 is installed inside the guide ring 7 through the motor bracket 9, and the impeller and the shaft are sealed by a sealing structure, wherein the impeller is the livestock impeller described above.

[0041] Furthermore, the sealing structure is an oil-sealed structure using a sealing ring and an outer cover.

[0042] Furthermore, the motor bracket 9 has a "T" shaped structure.

[0043] The "T" shaped structure is beneficial to the stability of the fan and reduces its vibration.

[0044] Furthermore, the inner wall of the guide ring 7 is provided with a guide structure 10 along the flow path direction, and the cross-sectional curve formed by the radial section of the guide structure 10 after unfolding is a sine curve or a cosine curve.

[0045] Furthermore, the axial length of the impeller is W1, the inlet end of the guide structure 10 coincides with the foremost front end of the radial projection of the impeller on the inner wall of the guide ring 7, and the axial length of the guide structure 10 is W2, where W2 = (0.3~0.8)W1.

[0046] The stability of the flow pattern at the leading edge of the fan directly determines the occurrence of noise and surge. This application addresses this by incorporating a flow-guiding structure with a sine or cosine curve in its cross-section, and an axial length less than that of the impeller. This structure acts as a streamlined flow-guiding noise reduction component, suppressing the development of vortices from the fan blades, thereby reducing flow kinetic energy loss and fan noise. It also improves the uniformity of the fan flow field and enhances fan efficiency. The axial length of the flow-guiding structure is not equal to that of the impeller to minimize its impact on the outlet end and further improve conveying efficiency.

[0047] This invention discloses an impeller for livestock use, comprising an inner hub, inner large blades, inner small blades, an outer hub, and outer blades. The inner large blades and inner small blades are alternately and evenly arranged on the outer ring of the inner hub. The inner ring of the outer hub is fixed to the tip of the inner large blades. The outer blades are evenly arranged on the outer ring of the outer hub. The inner large blades, inner small blades, and outer blades are all composite blades. The inner large blades are straight blades near the inner hub and curved / twisted blades near the outer hub. The outer blades are curved / twisted blades near the outer hub and straight blades away from the outer hub. The inner small blades and outer blades are geometrically similar in structure. Flow stabilizing holes are provided on the outer hub between adjacent outer blades, and the centerline of the flow stabilizing holes is not collinear with the impeller center. The radius of the outer hub is R, the outer radius of the curved / twisted portion of the outer blade is R2, and the inner radius of the curved / twisted portion of the inner large blade is R1, where R2 = (1.3~1.5)R and R1 = (0.6~0.9)R. Improvements to the impeller and blade structure effectively increase wind pressure, reduce noise, enhance stability, reduce surge, and increase efficiency.

Claims

1. An impeller for livestock use, comprising an inner hub (1), inner large blades (2), inner small blades (3), an outer hub (4), and outer blades (5), wherein the inner large blades (2) and inner small blades (3) are alternately and evenly arranged on the outer ring of the inner hub (1), the inner ring of the outer hub (4) is fixed to the tip of the inner large blades (2), and the outer blades (5) are evenly arranged on the outer ring of the outer hub (4), characterized in that: The inner large blade (2), inner small blade (3), and outer blade (5) are all composite blades; the inner large blade (2) uses a straight blade on the side near the inner hub (1) and a curved / twisted blade on the side near the outer hub (4); the outer blade (5) uses a curved / twisted blade on the side near the outer hub (4) and a straight blade on the side away from the outer hub (4); the inner small blade (3) and the outer blade (5) are geometrically similar in structure; each outer hub (4) between adjacent outer blades (5) is provided with a flow stabilizing hole (6), and the center line of the flow stabilizing hole (6) is parallel to the outer hub (4). The impeller centers are not collinear; the radius of the outer hub (4) is R, the outer radius of the bent part of the outer blade (5) is R2, and the inner radius of the bent part of the inner large blade (2) is R1, where R2 = (1.3~1.5)R and R1 = (0.6~0.9)R; the angle between the center line of the flow stabilizing hole (6) and the radius line at that position is A, where A = 10°~60°; the tip radius of the inner small blade (3) is R3, where R3 = (0.3~0.6)R; the position of the flow stabilizing hole (6) is closer to the trailing edge of the outer blade (5).

2. The livestock impeller as described in claim 1, characterized in that, The chord length corresponding to the outer side of the twisted part of the outer blade (5) is L1, and the chord length corresponding to the inner side of the twisted part of the inner large blade (2) is L2, where L1 > L2 and L1 = (1.1~1.3)L2.

3. The livestock impeller as described in claim 1, characterized in that, The impeller surface is covered with a wear-resistant and corrosion-resistant composite film.

4. The livestock impeller as described in claim 3, characterized in that, The composite membrane is made of fiberglass.

5. A negative pressure fan, characterized in that, The fan includes a guide ring (7), a motor (8), a motor bracket (9), and a shaft sealing structure. The impeller is fixed to the end of the motor (8). The motor (8) is installed inside the guide ring (7) through the motor bracket (9). The impeller and the shaft are sealed by a sealing structure. The impeller is the livestock impeller as described in any one of claims 1 to 4.

6. A negative pressure fan as described in claim 5, characterized in that, The sealing structure is an oil-sealed structure using a sealing ring and an outer cover.

7. A negative pressure fan as described in claim 5, characterized in that, The motor bracket (9) has a "T" shaped structure.

8. A negative pressure fan as described in claim 5, characterized in that, The inner wall of the guide ring (7) is provided with a guide structure (10) along the flow path direction. The cross-sectional curve formed by the radial section of the guide structure (10) after unfolding is a sine curve or a cosine curve.

9. A negative pressure fan as described in claim 8, characterized in that, The axial length of the impeller is W1. The inlet end of the guide structure (10) coincides with the front end of the radial projection of the impeller on the inner wall of the guide ring (7). The axial length of the guide structure (10) is W2, where W2 = (0.3~0.8)W1.

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