Industrial fan

Abstract

The invention belongs to the technical field of blowing devices, and provides an industrial fan which comprises a fan shell, an impeller assembly and an air inlet drainage assembly, and the air inlet drainage assembly comprises a first flow stabilizing section, a second flow stabilizing section, a first compression section and a second compression section which are different in diameter. And the through-flow sections of the first steady flow section, the second steady flow section, the first compression section and the second compression section are smoothly connected in sequence. Compared with the prior art, by improving the sizes of the first steady flow section, the second steady flow section, the first compression section and the second compression section, the Coanda effect can be effectively utilized, the whole flow channel can achieve good wall-attached laminar flow, air flow can flow more smoothly in the rotating process of the impeller assembly, air flow can be effectively guided, and the air flow efficiency is improved. The backflow and turbulent flow phenomena of air in the machine shell are reduced, the efficiency of the fan is effectively improved, and aerodynamic noise is reduced.

Description

Technical Field

[0001] The present invention belongs to the technical field of blowing devices, and particularly relates to an industrial fan. Background Art

[0002] As a necessity in industrial production, fans are widely used in industrial production and are always in an on state during normal production processes. The energy consumption of fans accounts for 10%-15% of the total energy consumption in industrial production. The operating efficiency of the fan system directly affects the energy consumption level and production cost of production. At the same time, most industrial fans have high operating noise due to rough and unreasonable designs, which also has a great impact on the working environment. Therefore, designing a fan system with higher total pressure efficiency and lower noise is crucial for industrial production and has significant economic and social value.

[0003] At present, many fans used in industry have much room for optimization and improvement in terms of structural layout, flow channel design, blade design, and material selection. For example, the patent - an energy-saving and efficient fan based on improving operating efficiency (CN113217419A) proposes an energy-saving fan solution, but there is much room for optimization in its air inlet design, blade structure, and volute part. Another example is the patent - an energy-saving fan blade (CN222615660U) which discloses an energy-saving fan blade, but this solution has poor processability and high production difficulty, and is not convenient for industrial-scale production. Summary of the Invention

[0004] The technical problem to be solved by the present invention is to provide an industrial fan in view of the current situation of the prior art.

[0005] The technical solution adopted by the present invention to solve the above technical problem is to propose an industrial fan, comprising: a fan housing, which includes an air inlet and an air outlet;

[0006] An impeller assembly, which is arranged inside the fan housing and includes a diversion channel and an exhaust duct, and the exhaust duct is used to introduce fluid to the air outlet;

[0007] The air inlet diversion assembly is fixed on the fan housing and located at the air inlet. The air inlet diversion assembly includes a first flow stabilization section, a second flow stabilization section, a first compression section, and a second compression section with different diameters. The flow-through cross-sections of the first flow stabilization section, the second flow stabilization section, the first compression section, and the second compression section are smoothly connected in sequence. The inner diameter of the first flow stabilization section is D1 and the axial length is H1. The second flow stabilization section is in the shape of a hollow frustum of a cone, with the maximum inner diameter equal to that of the first flow stabilization section, the minimum inner diameter equal to the inner diameter of the first compression section, and the axial length is H2. The inner diameter of the first compression section is D3 and the axial length is H3. The second compression section extends into the diversion channel and is in clearance fit with the inner wall of the diversion channel, with the maximum inner diameter being D2 and the axial length being H4; where,

[0008] The air flow compression angle of the air inlet diversion assembly, that is,

[0009]

[0010] At the same time, H1:H2 ∈ [0.5, 0.8], H3:H2 ∈ [0.85, 1.2], and the value of H4 is more than 10 millimeters.

[0011] In the above-mentioned industrial fan, the clearance between the second compression section and the impeller assembly is 1 to 3 millimeters.

[0012] In the above-mentioned industrial fan, the fan housing is in the shape of a volute, which includes a front cover plate and a rear cover plate arranged oppositely, and the two are connected by a side plate. The impeller assembly includes an impeller front panel and an impeller back panel arranged oppositely, and a plurality of blades arranged between the two. The impeller front panel is arranged on the side facing the air inlet diversion assembly. The distance between the impeller back panel and the rear cover plate is H5. The maximum distance between the impeller front panel and the front cover plate is H6. The distance between the front cover plate and the rear cover plate is H7. The thickness of the end of the blade far from the center of the impeller back panel is H10; where,

[0013] H7 = H6 + H5 + H10,

[0014] At the same time, H6:H7 ∈ [0.5, 0.7], H10:H7 ∈ [0.23, 0.33], and the value of H5 is more than 10 millimeters.

[0015] In the above-mentioned industrial fan, the blade sequentially includes a first section, a second section, and a third section from the center of the impeller back panel outwards. The thickness of the first section is H8, the thickness of the second section is H9, and the thickness of the third section is H10; where,

[0016] H8:H10 ∈ [1.2, 1.6], H9:H10 ∈ [1, 1.2].

[0017] In the above-mentioned industrial fan, for one end of two adjacent blades facing the center of the impeller back plate, the connecting line with the center of the impeller back plate forms a first included angle, and for the end far from the center of the impeller back plate, the connecting line with the center of the impeller back plate forms a second included angle. For one end of the same blade facing the center of the impeller back plate and the end far from the center of the impeller back plate, the connecting lines with the center of the impeller back plate form a third included angle. The first included angle is θ1, the second included angle is θ2, and the third included angle is θ3; wherein,

[0018] θ1 = θ2; θ1 ∈ [25°, 43°]; θ3 ∈ [43°, 63°].

[0019] In the above-mentioned industrial fan, the blades are arc-shaped, with a radius of R3. One ends of multiple blades far from the center of the impeller back plate are all located on the same circle, and the radius of this circle is R2. One ends of multiple blades close to the center of the impeller back plate are all located on the same circle, and the radius of this circle is R1. The radius of the diversion channel is R4; wherein,

[0020] R3:R2 ∈ [1.25, 1.65], R3:R1 ∈ [3.3, 3.7], R1:R4 ∈ [0.6, 0.9].

[0021] In the above-mentioned industrial fan, it further includes a first flange and a second flange. The first flange is connected to one end of the air inlet diversion assembly far from the impeller assembly, and the second flange is connected to the air outlet.

[0022] In the above-mentioned industrial fan, the impeller assembly includes a rotating shaft, and one end of the rotating shaft penetrates through the fan housing.

[0023] In the above-mentioned industrial fan, reinforcing ribs are arranged on both the front cover plate and the rear cover plate.

[0024] In the above-mentioned industrial fan, the impeller front panel, the impeller back plate and the blades are connected by welding.

[0025] Compared with the prior art, the present invention has the following beneficial effects:

[0026] (1) Through the improvement of the dimensions of the first steady flow section, the second steady flow section, the first compression section and the second compression section, the Coandă effect can be effectively utilized, and a good wall-attached laminar flow can be achieved in the overall flow channel, so that the air flow can flow more smoothly during the rotation of the impeller assembly, effectively guiding the gas flow, reducing the backflow and turbulence phenomena of the gas in the casing, reducing the flow loss, and improving the static pressure efficiency of the fan. Such a progressive compression and diversion structure can effectively reduce the adverse effects of separated flow, vortex, secondary flow, etc. on the aerodynamic performance, effectively improving the efficiency of the fan and reducing the aerodynamic noise.

[0027] (2) By designing the size and structure of the impeller assembly, the air in the air inlet pipe network can be smoothly introduced into the blades, effectively stabilizing the air flow, preventing air flow turbulence, thus significantly reducing the aerodynamic noise at the air inlet position and improving the total pressure efficiency of the fan system at the same time.

[0028] (3) The blade thickness is designed according to the ratio of H8:H10 ∈ [1.2, 1.6] and H9:H10 ∈ [1, 1.2], which helps to improve the air flow distribution, enhance the guiding effect on the air flow, and further improve the efficiency and stability of the fan. Brief Description of the Drawings

[0029] Figure 1 is a perspective view of an industrial fan of the present invention.

[0030] Figure 2 is a perspective view of the fan housing.

[0031] Figure 3 is Figure 1 a cross-sectional view of

[0032] Figure 4 is a perspective view of the air inlet diversion assembly.

[0033] Figure 5 is a perspective view of the impeller assembly.

[0034] Figure 6 is a plan view of the impeller assembly.

[0035] Figure 7 is a plan view when the blade is installed on the impeller back plate.

[0036] In the figure, 100, fan housing; 110, air inlet; 120, air outlet; 130, front cover plate; 140, rear cover plate; 150, side plate; 160, first flange; 170, second flange; 180, reinforcing rib; 200, impeller assembly; 210, diversion channel; 220, exhaust duct; 230, impeller front panel; 240, impeller back plate; 250, blade; 251, first section; 252, second section; 253, third section; 260, rotating shaft; 300, air inlet diversion assembly; 310, first steady flow section; 320, second steady flow section; 330, first compression section; 340, second compression section. Detailed Embodiments

[0037] The following are specific embodiments of the present invention and in combination with the drawings, the technical solutions of the present invention are further described, but the present invention is not limited to these embodiments.

[0038] It should be noted that all directional indications (such as up, down, left, right, front, back...) in the embodiments of the present invention are only used to explain the relative positional relationship and movement conditions between components in a specific posture (as shown in the attached drawings). If the specific posture changes, the directional indications will also change accordingly.

[0039] As Figures 1 to 7 shown, an industrial fan of the present invention includes: a fan housing 100, an impeller assembly 200, and an air inlet diversion assembly 300.

[0040] Specifically, the fan housing 100 includes an air inlet 110 and an air outlet 120; the impeller assembly 200 is disposed inside the fan housing 100, and includes a diversion channel 210 and an exhaust duct 220. The exhaust duct 220 is used to introduce fluid into the air outlet 120; the air inlet diversion assembly 300 is fixed on the fan housing 100 and is located at the air inlet 110. The air inlet diversion assembly 300 includes a first steady flow section 310, a second steady flow section 320, a first compression section 330, and a second compression section 340 with different diameters. The flow-through cross-sections of the first steady flow section 310, the second steady flow section 320, the first compression section 330, and the second compression section 340 are smoothly connected in sequence. The inner diameter of the first steady flow section 310 is D1 and the axial length is H1. The second steady flow section 320 is in the shape of a hollow frustum of a cone, with the maximum inner diameter equal to that of the first steady flow section 310, the minimum inner diameter equal to the inner diameter of the first compression section 330, and the axial length of H2. The inner diameter of the first compression section 330 is D3 and the axial length is H3. The second compression section 340 extends into the diversion channel 210 and is in clearance fit with the inner wall of the diversion channel 210, and the maximum inner diameter is D2 and the axial length is H4; wherein, the air flow compression angle of the air inlet diversion assembly 300, that is At the same time, H1:H2 ∈ [0.5, 0.8], H3:H2 ∈ [0.85, 1.2], and the value of H4 is more than 10 millimeters.

[0041] The air inlet diversion assembly 300 is preferably fixed on the fan housing 100 by welding. One end of the air inlet diversion assembly 300 away from the fan housing 100 is connected to the air inlet pipe network through a first flange 160, and the air outlet 120 is connected to the air supply pipe network through a second flange 170. During operation, the impeller assembly 200 rotates and compresses the air flow entering the fan housing 100 from the air inlet diversion assembly 300 through the first compression section 330 and the second compression section 340 in sequence, so that the air flow is discharged from the air outlet 120 after passing through the exhaust duct 220.

[0042] In this solution, by improving the dimensions of the first steady flow section 310, the second steady flow section 320, the first compression section 330, and the second compression section 340, the Coandă effect can be effectively utilized, enabling a good attached wall laminar flow in the overall flow channel. This not only allows the air flow to move more smoothly during the rotation of the impeller assembly 200, but also effectively guides the gas flow, reduces the backflow and turbulence of the gas in the casing, reduces the flow loss, and improves the static pressure efficiency of the fan. Such a progressive compression and drainage structure can effectively reduce the adverse effects of separated flow, vortices, secondary flow, etc. on the aerodynamic performance, thereby improving the efficiency of the fan and reducing the aerodynamic noise.

[0043] Preferably, the gap between the second compression section 340 and the impeller assembly 200 is maintained within the range of 1 to 3 millimeters to ensure that the impeller assembly 200 does not interfere with the air inlet drainage assembly 300 during rotation and to ensure the normal operation of the impeller assembly 200.

[0044] It is worth mentioning that the fan casing 100 is in a volute shape and includes a front cover plate 130 and a rear cover plate 140 arranged oppositely, which are connected by a side plate 150. The impeller assembly 200 includes an impeller front panel 230 and an impeller back panel 240 arranged oppositely, and a plurality of blades 250 arranged between the two. The impeller front panel 230 is located on the side facing the air inlet drainage assembly 300. The distance between the impeller back panel 240 and the rear cover plate 140 is defined as H5, the maximum distance between the impeller front panel 230 and the front cover plate 130 is defined as H6, the distance between the front cover plate 130 and the rear cover plate 140 is defined as H7, and the thickness of one end of the blade 250 far from the center of the impeller back panel 240 is defined as H10; wherein, H7 = H6 + H5 + H10, and the ratio range of H6:H7 is between [0.5, 0.7], the ratio range of H10:H7 is between [0.23, 0.33], and the value of H5 should be more than 10 millimeters.

[0045] The design of the volute-shaped fan casing 100 structure and the specific dimension relationship (such as H6:H7 ∈ [0.5, 0.7]) can optimize the air flow channel, make the gas flow more smoothly, reduce the backflow and turbulence phenomena, and improve the overall performance and efficiency of the fan. In this solution, through the design of the above-mentioned dimension structure of the impeller assembly 200, the air in the air inlet pipe network can be smoothly introduced into the blades 250, effectively stabilizing the air flow and preventing the air flow from being turbulent, thereby significantly reducing the aerodynamic noise at the air inlet 110 position and improving the total pressure efficiency of the fan system.

[0046] Further, the blade 250 sequentially includes a first section 251, a second section 252, and a third section 253 from the center of the impeller backplate 240 outwards. The thickness of the first section 251 is H8, the thickness of the second section 252 is H9, and the thickness of the third section 253 is H10. Among them, H8:H10 ∈ [1.2, 1.6], and H9:H10 ∈ [1, 1.2].

[0047] The thickness of the blade 250 is designed according to the ratio of H8:H10 ∈ [1.2, 1.6] and H9:H10 ∈ [1, 1.2], which helps to improve the air flow distribution, enhance the guiding effect on the air flow, and further improve the efficiency and stability of the fan.

[0048] In this solution, at one end of two adjacent blades 250 facing the center of the impeller backplate 240, the connection line with the center of the impeller backplate 240 forms a first included angle, and at the end far from the center of the impeller backplate 240, the connection line with the center of the impeller backplate 240 forms a second included angle. For the same blade 250, the connection lines of the end facing the center of the impeller backplate 240 and the end far from the center of the impeller backplate 240 with the center of the impeller backplate 240 form a third included angle. The first included angle is θ1, the second included angle is θ2, and the third included angle is θ3. Among them, θ1 = θ2; θ1 ∈ [25°, 43°]; θ3 ∈ [43°, 63°].

[0049] By precisely controlling the angles of the blade 250 (θ1 = θ2; θ1 ∈ [25°, 43°]; θ3 ∈ [43°, 63°]), the air flow can be guided more effectively, energy loss can be reduced, and at the same time, it also helps to reduce the noise level and improve the working efficiency of the fan.

[0050] It is worth mentioning that the blade 250 is arc-shaped with a radius of R3. The ends of multiple blades 250 far from the center of the impeller backplate 240 are all located on the same circle with a radius of R2, and the ends of multiple blades 250 close to the center of the impeller backplate 240 are all located on the same circle with a radius of R1. The radius of the flow guiding channel 210 is R4. Among them, R3:R2 ∈ [1.25, 1.65], R3:R1 ∈ [3.3, 3.7], and R1:R4 ∈ [0.6, 0.9].

[0051] The blade 250 is arc-shaped and its radius ratio (R3:R2 ∈ [1.25, 1.65], R3:R1 ∈ [3.3, 3.7], R1:R4 ∈ [0.6, 0.9]) is carefully designed so that the air flow can form a good laminar flow state inside the impeller, enhancing the air suction and exhaust capacity of the fan and improving the overall efficiency.

[0052] In this solution, the impeller assembly 200 includes a rotating shaft 260, and one end of the rotating shaft 260 penetrates through the fan housing 100.

[0053] The rotating shaft 260 passing through this end of the fan housing 100 is used to connect an external driving device (such as a motor) to drive the impeller assembly 200 to rotate.

[0054] Preferably, reinforcing ribs 180 are provided on both the front cover plate 130 and the rear cover plate 140. The provision of the reinforcing ribs 180 on the front cover plate 130 and the rear cover plate 140 increases the strength and stiffness of the fan housing 100, prevents deformation, and improves the durability and safety of the equipment.

[0055] Preferably, the impeller front panel 230, the impeller back panel 240 and the blades 250 are connected by welding.

[0056] The impeller front panel 230, the impeller back panel 240 and the blades 250 are connected by welding, which enhances the firmness between components, avoids the risk of loosening or separation, and ensures long-term stable operation.

[0057] It should be noted that in the present invention, descriptions such as "first", "second", "one", etc. are only for descriptive purposes and should not be construed as indicating or implying their relative importance or implicitly indicating the quantity of the indicated technical features. Thus, features defined with "first" and "second" may explicitly or implicitly include at least one of such features. In the description of the present invention, the meaning of "a plurality" is at least two, such as two, three, etc., unless otherwise specifically defined. Terms such as "connection" and "fixation" should be understood in a broad sense. For example, "fixation" can be a fixed connection, a detachable connection, or integrated; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and can be the internal communication of two elements or the interaction relationship between two elements, unless otherwise clearly defined. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0058] In addition, the technical solutions between various embodiments of the present invention can be combined with each other, but it must be based on what can be achieved by those of ordinary skill in the art. When the combination of technical solutions is contradictory or cannot be achieved, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection required by the present invention.

[0059] The specific embodiments described herein are only illustrative of the spirit of the present invention. Those skilled in the art of the present invention can make various modifications or supplements to the described specific embodiments or use similar ways to replace them, but will not deviate from the spirit of the present invention or exceed the scope defined by the appended claims.

Claims

1. An industrial fan, characterized in that: include: A fan housing, comprising an air inlet and an air outlet; An impeller assembly, which is disposed in the fan housing and includes a flow channel and an exhaust channel, wherein the exhaust channel is used to introduce the fluid into the air outlet; An air inlet drainage component is fixed on the fan housing and located at the air inlet, the air inlet drainage component includes a first steady flow section, a second steady flow section, a first compression section and a second compression section of different diameters, the flow cross sections of the first steady flow section, the second steady flow section, the first compression section and the second compression section are smoothly connected in sequence, the inner diameter of the first steady flow section is D1 and the axial length is H1, the second steady flow section is a hollow frustum, the maximum inner diameter is equal to that of the first steady flow section, the minimum inner diameter is equal to that of the first compression section, and the axial length is H2, the inner diameter of the first compression section is D3 and the axial length is H3, the second compression section extends into the drainage channel and cooperates with the inner wall gap of the drainage channel, and the maximum inner diameter is D2 and the axial length is H4; wherein, The airflow compression angle of the air inlet guide assembly is Meanwhile, H1:H2∈[0.5,0.8], H3:H2∈[0.85,1.2], and H4 are above 10 mm.

2. An industrial fan according to claim 1, characterized in that: The gap between the second compression section and the impeller assembly is 1 to 3 mm.

3. An industrial fan according to claim 1, characterized in that: The fan housing is in the shape of a volute, and includes a front cover plate and a rear cover plate that are arranged opposite to each other, and the two are connected by a side plate. The impeller assembly includes an impeller front panel and an impeller back plate that are arranged opposite to each other, and a plurality of blades arranged therebetween. The impeller front panel is arranged on the side facing the air inlet guide assembly, the distance between the impeller back plate and the rear cover plate is H5, the maximum distance between the impeller front panel and the front cover plate is H6, the distance between the front cover plate and the rear cover plate is H7, and the thickness of the blade at one end away from the center of the impeller back plate is H10; wherein, H7=H6+H5+H10, Meanwhile, H6:H7∈[0.5,0.7], H10:H7∈[0.23,0.33], and the value of H5 is above 10 mm.

4. An industrial fan according to claim 3, characterized in that: The blade includes a first section, a second section and a third section from the center of the impeller back plate outward in sequence, the thickness of the first section is H8, the thickness of the second section is H9, and the thickness of the third section is H10; wherein, H8:H10∈[1.2,1.6], H9:H10∈[1,1.2].

5. An industrial fan as claimed in claim 3, characterized in that: One end of two adjacent blades facing the center of the impeller back plate forms a first angle with the line connecting the center of the impeller back plate, and one end away from the center of the impeller back plate forms a second angle with the line connecting the center of the impeller back plate. The line connecting one end of the same blade facing the center of the impeller back plate and one end away from the center of the impeller back plate forms a third angle with the line connecting the center of the impeller back plate. The first angle is θ1, the second angle is θ2, and the third angle is θ3; wherein, θ1=θ2; θ1∈[25°,43°]; θ3∈[43°,63°].

6. An industrial fan according to claim 3, characterized in that: The blades are arc-shaped, and their radius is R3. The ends of the plurality of blades away from the center of the impeller back plate are all located on the same circle, and the radius of the circle is R2. The ends of the plurality of blades close to the center of the impeller back plate are all located on the same circle, and the radius of the circle is R1. The radius of the drainage channel is R4. R3:R2∈[1.25,1.65], R3:R1∈[3.3,3.7], R1:R4∈[0.6,0.9].

7. An industrial fan according to claim 1, characterized in that: It also includes a first flange and a second flange, wherein the first flange is connected to one end of the air inlet guide assembly away from the impeller assembly, and the second flange is connected to the air outlet.

8. An industrial fan according to claim 1, characterized in that: The impeller assembly comprises a rotating shaft, one end of which passes through the fan housing.

9. An industrial fan according to claim 1, characterized in that: The front cover plate and the rear cover plate are both provided with reinforcing ribs.

10. An industrial fan according to claim 1, characterized in that: The impeller front panel, the impeller back panel and the blades are connected by welding.

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