WO2021063050A1 - Fan and axial-flow impeller - Google Patents

Fan and axial-flow impeller Download PDF

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Publication number
WO2021063050A1
WO2021063050A1 PCT/CN2020/098689 CN2020098689W WO2021063050A1 WO 2021063050 A1 WO2021063050 A1 WO 2021063050A1 CN 2020098689 W CN2020098689 W CN 2020098689W WO 2021063050 A1 WO2021063050 A1 WO 2021063050A1
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WO
WIPO (PCT)
Prior art keywords
blade
hub
axial flow
flow impeller
blade tip
Prior art date
Application number
PCT/CN2020/098689
Other languages
French (fr)
Chinese (zh)
Inventor
梁浩
柳洲
陈宇强
林海利
Original Assignee
珠海格力电器股份有限公司
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Application filed by 珠海格力电器股份有限公司 filed Critical 珠海格力电器股份有限公司
Publication of WO2021063050A1 publication Critical patent/WO2021063050A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow fans
    • F04D29/327—Rotors specially for elastic fluids for axial flow pumps for axial flow fans with non identical blades
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38—Blades
    • F04D29/384—Blades characterised by form
    • F04D29/386—Skewed blades

Definitions

  • This application relates to the technical field of fans, in particular to a fan and an axial flow impeller.
  • An axial flow impeller comprising a first blade, the first blade comprising a plurality of first blades and a first hub, the plurality of first blades are arranged on the first hub at intervals; the first The blade includes a first blade root and a first blade tip, the first blade root is the part where the first blade contacts the first hub, and the first blade tip is the first blade far away from the The part of the first blade root, the line between the opposite ends of the first blade tip is the chord line of the first blade tip, and the first blade tip is away from the chord line of the first blade tip The direction of the blade is bent so that the pressure surface of the first blade is located at the first blade tip as an inner concave surface, and the first blade root smoothly transitions to the first blade tip.
  • the first blade includes a first blade root and a first blade tip, wherein the first blade root is a part where the first blade contacts the first hub, and the first blade tip is a part away from the first blade root.
  • the first blade tip is bent in a direction away from the chord line of the first blade tip, so that the pressure surface of the first blade located at the first blade tip is a concave surface, which can improve the work efficiency of the pressure surface of the first blade.
  • the load of the wind on the first blades is reduced, so that the power of the first blades is reduced, thereby reducing the power of the axial flow impeller.
  • the first blade root smoothly transitions to the first blade tip, which can effectively improve the smoothness of the first blade's air guide and improve the comfort of air supply.
  • the opposite ends of the first blade near the first blade tip portion respectively form a first blade tip and a first blade tail
  • the rounded size of the outer edge of the first blade tip is R1
  • the rounded size of the outer edge of the first blade tail is R2, where R2>R1.
  • the fillet size R1 of the outer edge of the first blade tip is 2 mm to 8 mm; or
  • the fillet size R2 of the outer edge of the first blade tail is 30mm-50mm.
  • the round corner size R1 of the outer edge of the first blade tip is 2 mm to 8 mm;
  • the fillet size R2 of the outer edge of the first blade tail is 30mm-50mm.
  • the first blade tail is curved toward the pressure surface of the first blade to form a swept portion.
  • the included angle ⁇ between the swept portion and the tangent plane of the first blade tip is 0°-15°.
  • the installation angle of the first blade root relative to the axis of the first hub is ⁇ 1
  • the installation angle of the first blade tip relative to the axis of the first hub is ⁇ 2, where , ⁇ 2> ⁇ 1.
  • the installation angle ⁇ 1 of the first blade root relative to the axis of the first hub is 40°-60°; or
  • the installation angle ⁇ 2 of the first blade tip relative to the axis of the first hub is 60°-75°.
  • the installation angle ⁇ 1 of the first blade root relative to the axis of the first hub is 40°-60°;
  • the installation angle ⁇ 2 of the first blade tip relative to the axis of the first hub is 60°-75°.
  • the line between opposite ends of the first blade root is the chord line of the first blade root
  • the chord length of the first blade root chord line is L1
  • the first blade tip The chord length of the string is L2, where L2>L1.
  • chord length L1 of the first blade root chord line is 40mm-60mm; or
  • the chord length L2 of the first blade tip chord line is 60 mm to 80 mm.
  • the chord length L1 of the first blade root chord line is 40mm-60mm;
  • the chord length L2 of the first blade tip chord line is 60 mm to 80 mm.
  • it further includes a second wind blade, the inner wall of the first hub encloses an installation cavity, and the second wind blade is arranged in the installation cavity.
  • the second wind blade includes a plurality of second blades and a second hub, and the plurality of second blades are arranged on the second hub at intervals;
  • the ratio of the diameter D1 of the second hub to the outer diameter D2 of the second blade is 0.2-0.3; and/or the outer diameter D2 of the second blade and the outer diameter of the first blade
  • the ratio of the diameter dimension D3 is 0.5 to 0.7.
  • the part of the second blade in contact with the second hub forms a second blade root
  • the second blade further has a second blade tip
  • the second blade tip is away from the
  • the installation angle of the second blade root relative to the axis of the second hub is ⁇ 3
  • the installation angle of the second blade tip relative to the axis of the second hub is ⁇ 4, where , ⁇ 4> ⁇ 3.
  • the installation angle ⁇ 3 of the second blade root relative to the axis of the second hub is 30°-50°;
  • the installation angle ⁇ 4 of the second blade tip relative to the axis of the second hub is 60°-75°.
  • the line between the opposite ends of the second blade root is the chord line of the second blade root, the chord length of the second blade root chord is L3, and the second blade root chord has a chord length of L3.
  • the line between the opposite ends of the blade tip is the chord line of the second blade tip, and the chord length of the second blade tip chord line is L4, where L4>L3.
  • chord length L3 of the second blade root chord line is 20mm-40mm; or
  • chord length L4 of the second blade tip chord line is 50mm-70mm.
  • chord length L3 of the second blade root chord line is 20mm-40mm;
  • chord length L4 of the second blade tip chord line is 50mm-70mm.
  • the first wind blade and the second wind blade are integrally formed.
  • a fan including:
  • the rotating member is used to drive the axial flow impeller to rotate.
  • the rotating part drives the axial flow impeller to rotate, so as to realize the air supply of the fan.
  • the first blade includes a first blade root and a first blade tip, the first blade root is the part where the first blade contacts the first hub, and the first blade tip is a part away from the first blade root.
  • the first blade tip is bent in a direction away from the chord line of the first blade tip, so that the pressure surface of the first blade located at the first blade tip is a concave surface, which can improve the work efficiency of the pressure surface of the first blade.
  • the load of the wind on the first blade is reduced, so that the power of the first blade is reduced, thereby reducing the power of the axial flow impeller, so that the fan is more energy-saving.
  • the first blade root smoothly transitions to the first blade tip, which can effectively improve the smoothness of the first blade's air guide and improve the comfort of the fan.
  • Figure 1 is a front view of an axial flow impeller in an embodiment
  • Figure 2 is a side view of the axial flow impeller shown in Figure 1;
  • Figure 3 is an enlarged view of A in Figure 2;
  • Figure 4 is a front view of the second fan blade in Figure 1;
  • Figure 5 is a side view of the second wind blade shown in Figure 4.
  • Fig. 6 is a velocity cloud diagram of the axial flow impeller shown in Fig. 1.
  • Axial impeller 100, first blade, 110, first blade, 111, pressure surface, 112, first blade root, 114, first blade tip, 115, first blade tip, 116, first blade Tail, 118, swept part, 120, first hub, 200, second blade, 210, second blade, 212, second blade root, 220, second hub, 300, mounting part, 310, mating part, 320. Connecting part.
  • the axial flow impeller 10 in an embodiment can at least guarantee work and air supply air volume and air supply range when the power is reduced, so that the axial flow impeller 10 is more energy-saving.
  • the axial flow impeller 10 includes a first fan blade 100, the first fan blade 100 includes a plurality of first blades 110 and a first hub 120, and the plurality of first blades 110 are arranged on the first hub 120 at intervals; the first blades 110 includes a first blade root 112 and a first blade tip 114, the first blade root 112 is the part where the first blade 110 contacts the first hub 120, and the first blade tip 114 is the first blade 110 away from the first blade root 112
  • the line between the opposite ends of the first blade tip 114 is the chord line of the first blade tip 114, and the first blade tip 114 is bent in a direction away from the chord line of the first blade tip 114, so that the first blade tip 114
  • the portion where the pressure surface 111 of a blade 110 is located at the first blade tip 114 is an inner concave surface, and the first blade root 112 smoothly transitions to the first blade tip 114.
  • the pressure surface 111 of the first blade 110 is a surface facing the rotation direction of the first
  • the first blade 110 includes a first blade root 112 and a first blade tip 114, wherein the first blade root 112 is the contact part of the first blade 110 and the first hub 120, and the first blade tip 114 is away from the first blade.
  • the first blade tip 114 is bent in a direction away from the chord line of the first blade tip 114, so that the pressure surface 111 of the first blade 110 is located on the first blade tip 114 as a concave surface, which can increase the pressure of the first blade 110
  • the work efficiency of the surface 111 can reduce the load of the wind on the first blade 110 while ensuring the work of the first blade 110, so that the power of the first blade 100 is reduced, and thus the power of the axial flow impeller 10 is reduced.
  • the first blade root 112 smoothly transitions to the first blade tip 114, which can effectively improve the smoothness of the first blade 110 to guide the wind and improve the comfort of air supply.
  • the connecting line between the opposite ends of the first blade root 112 is the chord line of the first blade root 112, and the chord line of the first blade root 112 is away from the first blade root 112.
  • the direction of the line is set to bend.
  • the curvature of the first blade root 112 and the curvature of the first blade tip 114 may be the same or different, and the first blade root 112 smoothly transitions to the first blade tip 114.
  • the first blade root 112 may not be bent, and the first blade root 112 smoothly transitions to the first blade tip 114.
  • a/L2 is in the range of 0.03 to 0.06, the load of the first blade 110 can be reduced on the basis of ensuring the work of the first blade 110, thereby reducing the power of the first blade 100, so that the first blade 100 is in use. It is more energy-efficient.
  • the load of the first blade 110 will increase, which in turn will increase the power of the first blade 100, and the aerodynamic efficiency of the blade will be low; if the curvature of the second blade tip is If it is too large, the work efficiency of the first blade 110 may be low, the air volume becomes small, and the efficiency of the first blade 100 may decrease.
  • the ratio of a/L2 may be 0.03, 0.04, 0.05, or 0.06.
  • the opposite ends of the first blade 110 near the first blade tip 114 respectively form a first blade tip 115 and a first blade tail 116, and the rounded size of the outer edge of the first blade tip 115 R1, the rounded size of the outer edge of the first blade tail 116 is R2, where R2>R1.
  • the outer edge of the first blade tip 115 is set to a small rounded corner, and the first blade tip 115 is located at the front edge of the first blade 110, thereby reducing the impact of the first blade tip 115 on the incoming airflow and reducing the first blade tip 115 The eddy current of the tip 115 in turn reduces the generation of noise.
  • the outer edge of the first blade tail 116 is set with a larger rounded corner, and the larger rounded design can reduce the shedding of the wake vortex at the first blade tail 116, thereby reducing the flow of the wake vortex on the first blade tail 116. The influence of this can further reduce noise and improve sound quality.
  • the rounded corner size R1 of the outer edge of the first blade tip 115 is 2 mm to 8 mm, which effectively reduces the eddy current of the first blade tip 115, thereby effectively reducing noise.
  • the rounded corner size R1 of the outer edge of the first blade tip 115 may be 2 mm, 3 mm, 4 mm, 5 mm, 6 mm, 7 mm, 8 mm, or the like.
  • the rounded corner size R1 of the outer edge of the first blade tip 115 can also be adjusted according to the overall size of the first blade 110. For example, when the size of the first blade 110 is larger, the rounded size of the first blade tip 115 may be larger.
  • the fillet size R2 of the outer edge of the first blade tail 116 is 30 mm-50 mm, which effectively reduces the shedding of wake vortices and thereby reduces noise.
  • the fillet size R2 of the outer edge of the first blade tail 116 may be 30 mm, 40 mm, 50 mm, or the like.
  • the fillet size R2 of the outer edge of the first blade tail 116 can also be adjusted according to the overall size of the first blade 110. For example, when the size of the first blade 110 is larger, the fillet size of the first blade tail 116 may be larger.
  • the first blade tail 116 is bent toward the pressure surface 111 of the first blade 110 to form a swept portion 118, which can further reduce the shedding of wake vortices and increase the work of the swept portion 118 , And then increase the air volume.
  • the swept portion 118 can spread the air flow on the first blade 110 when it flows out, and increase the air supply range.
  • the swept portion 118 can also effectively reduce the fluid interference between the first blade tail 116 and the first blade tip 115 of the adjacent first blade 110, and avoid causing turbulence to form aerodynamic noise.
  • the angle ⁇ between the tangent plane of the swept portion 118 relative to the first blade tip 114 is 0°-15°. It can avoid the obvious increase of power while ensuring the increase of air volume.
  • the included angle ⁇ between the swept portion 118 and the tangent plane of the first blade tip 114 may be 0°, 5°, 10°, or 15°.
  • the tangent plane of the first blade tip 114 is the tangent plane of the most inflection point of the first blade tip 114.
  • the height between the swept portion 118 and the first blade root 112 is about one third of the distance between the first blade root 112 and the first blade tip 114. In turn, it is avoided that the swept portion 118 is too large to affect the energy efficiency ratio of the work performed by the first blade 110.
  • the installation angle of the first blade root 112 relative to the axis of the first hub 120 is ⁇ 1
  • the installation angle of the first blade tip 114 relative to the axis of the first hub 120 is ⁇ 2, where ⁇ 2> ⁇ 1 can be Ensure the work of the first blade 110. If ⁇ 2 ⁇ 1, the power of the first blade 110 will increase, but the work effect will be poor, and the work efficiency of the first blade 110 will decrease. At the same time, the load of the first blade 110 will increase, which will easily cause the first blade 110 to deform, which will affect the mission and stability of the axial flow impeller 10.
  • the installation angle ⁇ 1 of the first blade root 112 with respect to the axis of the first hub 120 is 40°-60°, thereby ensuring the work of the first blade 110 and avoiding an increase in power.
  • the installation angle ⁇ 1 may be 40°, 45°, 50°, 55°, or 60°.
  • the installation angle ⁇ 2 of the first blade tip 114 relative to the axis of the first hub 120 is 60° ⁇ 75°, which can ensure the work of the first blade 110 and avoid an increase in power.
  • the installation angle ⁇ 2 may be 60°, 65°, 70°, or 75°.
  • the chord length of the first blade root 112 is L1
  • the chord length of the first blade tip 114 is L2, where L2>L1.
  • chord length L1 of the chord line of the first blade root 112 is 40 mm-60 mm, which can effectively ensure the work area of the first blade 110 and avoid affecting the air distribution volume of the first blade 110.
  • chord length L2 of the chord line of the first blade tip 114 is 60 mm to 80 mm, which can further effectively ensure the work area of the first blade 110 and avoid affecting the air supply volume of the first blade 110.
  • the chord length L1 of the chord line of the first blade root 112 and the chord length L2 of the chord line of the first blade tip 114 may also be appropriately increased according to the increase in the overall size of the first blade 110, or according to The overall size of the first blade 110 is reduced appropriately.
  • the axial flow impeller 10 further includes a second fan blade 200, the inner wall of the first hub 120 encloses an installation cavity, and the second fan blade 200 is disposed in the installation cavity.
  • the structure of the first fan blade 100 can be further strengthened by arranging the second fan blade 200, so that the structure of the axial flow impeller 10 is more stable.
  • the second fan blade 200 by providing the second fan blade 200, the air volume and the air blowing range of the axial flow impeller 10 can be further increased.
  • the second wind blade 200 includes a plurality of second blades 210 and a second hub 220, and the plurality of second blades 210 are arranged on the second hub 220 at intervals.
  • the second blade 210 is driven to rotate by the second hub 220, so as to realize the air supply of the second blade 200.
  • the first fan blade 100 and the second fan blade 200 are integrally formed. Furthermore, the side of the second blade 210 away from the second hub 220 is fixed on the first hub 120, wherein the second hub 220 is used to connect the rotating member.
  • the first fan blade 100 can be further driven to rotate, so that the first fan blade 100 and the second fan blade 200 can rotate at the same time.
  • the first fan blade 100 and the second fan blade 200 are integrally injection molded, so that the structure of the axial flow impeller 10 is more stable.
  • the number of the first blades 110 is greater than or equal to the number of the second blades 210. Since the energy efficiency ratio of the first blade 100 is greater than that of the second blade 200, the number of the first blades 110 is set to be greater than or equal to the number of the second blades 210, which can effectively improve the axial flow impeller 10 The energy efficiency ratio of the overall work reduces power consumption.
  • the numbers of the first blades 110 and the second blades 210 are both odd numbers. Furthermore, it is avoided that the blades are symmetrically arranged, resulting in the symmetrical distribution of centrifugal force, wind resistance, etc. received by the first blade 110 and the second blade 210 during the rotation of the axial flow impeller 10, thereby causing the axial flow impeller 10 to be easily deformed. With the formation of asymmetrical distribution, the forces in different directions can cancel each other, reducing the force deformation on the first blade 100 and the second blade 200.
  • the number of first blades 110 is seven.
  • the number of second blades 210 is five.
  • the number of the first blades 110 can also be three, five, nine, etc.
  • the number of the second blades 210 can also be three, seven, or other numbers.
  • the ratio of the outer diameter D2 of the second blade 210 to the outer diameter D3 of the first blade 110 is 0.5-0.7.
  • the second wind blade 200 of the axial flow impeller 10 is the main work component, while the second wind blade 200 does relatively little work.
  • the ratio of the outer diameters of the second blade 210 to the first blade 110 the work area of the second blade 210 and the first blade 110 can be controlled.
  • the ratio of D2/D3 is larger, that is, the outer diameter of the second blade 210 is larger, the work area of the first blade 110 will be reduced.
  • the ratio of the outer diameter size of the first hub 120 to the outer diameter size D3 of the first blade 110 may be 0.55 to 0.65.
  • the wall thickness of the first hub 120 is 2 mm to 6 mm.
  • the first hub 120 is a bridge connecting the first blade 110 and the second blade 210.
  • the connection strength of the first blade 110 and the second blade 210 can be maintained, the stability of the structure can be improved, and the overall coordination of the axial flow impeller 10 can be improved.
  • the wall thickness of the first hub 120 is 4 mm.
  • the ratio of the diameter D1 of the second hub 220 to the outer diameter D2 of the second blade 210 is 0.2-0.3. On the one hand, it is ensured that the second hub 220 can be effectively connected to the rotating parts, and on the other hand, by controlling the ratio of the outer diameter of the second hub 220 to the second blade 210, the work and power of the second blade 210 can be effectively controlled.
  • the part where the second blade 210 is in contact with the second hub 220 forms a second blade root 212
  • the second blade 210 further has a second blade tip 214, and a second blade tip 214 Is the part of the second blade 210 away from the second blade root 212
  • the installation angle of the second blade root 212 relative to the axis of the second hub 220 is ⁇ 3
  • the installation angle of the second blade tip 214 relative to the axis of the second hub 220 is ⁇ 4, where ⁇ 4> ⁇ 3.
  • the installation angle ⁇ 3 of the second blade root 212 relative to the axis of the second hub 220 is 30°-50°.
  • the work of the second blade 210 can be ensured, and the increase in power can be avoided.
  • the installation angle ⁇ 3 may be 30°, 35°, 40°, 45°, or 50°.
  • the installation angle ⁇ 4 of the second blade tip 214 relative to the axis of the second hub 220 is 60° ⁇ 75°. It can ensure the work of the second blade 210 and avoid the increase of power. Specifically, the installation angle ⁇ 4 may be 60°, 65°, 70°, or 75°.
  • the line between the opposite ends of the second blade root 212 is the chord line of the second blade root 212, the chord length of the second blade root 212 is L3, and the second blade tip 214 has a chord length of L3.
  • the connecting line between is the chord line of the second blade tip 214, and the chord length of the second blade tip 214 is L4, where L4>L3.
  • chord length L3 of the chord line of the second blade root 212 is 20 mm-40 mm, which can further effectively reduce the power consumption of the second blade 210 and ensure a certain amount of work, thereby improving the energy efficiency ratio of the axial flow impeller 10.
  • chord length L4 of the chord line of the second blade tip 214 is 50 mm to 70 mm, which can further effectively reduce the power consumption of the second blade 210 and ensure a certain amount of work, thereby improving the energy efficiency ratio of the axial flow impeller 10.
  • the chord length of the chord line of the second blade root 212 and the chord length of the second blade tip 214 may also be appropriately increased according to the increase in the overall size of the second blade 200, or according to the second blade The overall size of the wind blade 200 is reduced appropriately.
  • the overall shape of the second blade 210 is slender, and the tip part of the second blade 210 resembles a swift wing, slender and round, which can reduce the power of the second blade 200 while ensuring the air volume, thereby reducing the power of the second blade 200.
  • the power of the axial flow impeller 10 is reduced, and the energy efficiency ratio of the axial flow impeller 10 is improved.
  • the air supply range is wide, and the wind spreads outward after meeting at a certain position, the wind field is wider, the air volume is larger, and the wind feel is softer and more comfortable.
  • the axial flow impeller 10 in the above embodiment can effectively reduce the "humming" during high-speed rotation and improve the sound quality.
  • the fan in one embodiment includes the axial flow impeller 10 in any of the above embodiments. Specifically, the fan further includes a rotating member for driving the axial flow impeller 10 to rotate. Further, the rotating member is arranged on the second hub 220. The rotating part is a motor.
  • the axial flow impeller 10 further includes a mounting member 300, the mounting member 300 is disposed in the second hub 220, and the rotating member is mounted on the mounting member 300.
  • the installation of the mounting member 300 can facilitate the installation of the rotating member, thereby facilitating the rotation of the axial flow impeller 10 through the rotating member.
  • the mounting member 300 includes a mating part 310 and a connecting part 320, and the mating part 310 is disposed on the second hub 220 through the connecting part 320.
  • the mating part 310 is used for mating with the rotating member.
  • the mating portion 310 is integrally formed on the inner wall of the second hub 220 through the connecting portion 320, which can improve the stability of the mounting member 300 on the second hub 220, thereby improving the stability of the rotating member on the axial flow impeller 10.
  • the fan is a floor-standing circulation fan. In other embodiments, the fan may also be other types of fans.

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  • General Engineering & Computer Science (AREA)
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Abstract

A fan and an axial-flow impeller (10). The axial-flow impeller (10) comprises a first fan blade (100); the first fan blade (100) comprises a plurality of first vanes (110) and a first hub (120); the plurality of first vanes (110) are arranged on the first hub (120) at intervals; each first vane (110) comprises a first vane root (112) and a first vane top (114), the first vane root (112) being a part of the first vane (110) in contact with the first hub (120), and the first vane top (114) being a part distant from the first vane root (112). The first vane top (114) is bent in a direction distant from a chord line of the first vane top (114) such that a part of a pressure surface of the first vane (110) located at the first vane top (114) is a concave surface. Therefore, the working efficiency of the pressure surface of the first vane (110) can be improved, the load of wind on the first vane (110) is reduced while working of the first vane (110) is guaranteed, the power of the first fan blade (100) is reduced, then the power of the axial-flow impeller (10) is reduced, and the fan becomes more energy-saving. Moreover, the first vane root (112) is in smooth transition with the first vane top (114), thereby effectively improving the air guide fluency of the first vane (110), and improving air supply comfort.

Description

风扇及轴流叶轮Fan and axial flow impeller
相关申请Related application
本申请要求2019年09月30日申请的，申请号为201910944315.4，名称为“风扇及轴流叶轮”的中国专利申请的优先权，在此将其全文引入作为参考。This application claims the priority of the Chinese patent application filed on September 30, 2019, the application number is 201910944315.4, titled "Fans and Axial Impellers", the full text of which is hereby incorporated by reference.
技术领域Technical field
本申请涉及风机技术领域，特别是涉及一种风扇及轴流叶轮。This application relates to the technical field of fans, in particular to a fan and an axial flow impeller.
背景技术Background technique
目前，传统的轴流风扇一般采用三个扇叶、五个扇叶、七个扇叶等数量的叶片实现送风。若为了保证轴流风扇的做功，往往通过增大扇叶的叶片的做功面积大来实现，进而导致负载重，功率高，导致不节能。At present, traditional axial fans generally use three blades, five blades, and seven blades to achieve air supply. If in order to ensure the work of the axial flow fan, it is often achieved by increasing the work area of the blades of the fan blades, which will lead to heavy load and high power, resulting in no energy saving.
发明内容Summary of the invention
基于此，有必要针对上述问题，提供一种保证做功能力，且避免增加功率消耗的风扇及轴流叶轮。Based on this, it is necessary to address the above-mentioned problems and provide a fan and axial flow impeller that can ensure functional performance and avoid increasing power consumption.
一种轴流叶轮，包括第一风叶，所述第一风叶包括多个第一叶片及第一轮毂，所述多个第一叶片间隔设置于所述第一轮毂上；所述第一叶片包括第一叶根与第一叶顶，所述第一叶根为所述第一叶片与所述第一轮毂相接触的部分，所述第一叶顶为所述第一叶片远离所述第一叶根的部分，所述第一叶顶的相对两端之间的连线为所述第一叶顶的弦线，所述第一叶顶向远离所述第一叶顶的弦线的方向弯曲设置，以使所述第一叶片的压力面位于所述第一叶顶的部分为内凹面，所述第一叶根平滑过渡至所述第一叶顶。An axial flow impeller, comprising a first blade, the first blade comprising a plurality of first blades and a first hub, the plurality of first blades are arranged on the first hub at intervals; the first The blade includes a first blade root and a first blade tip, the first blade root is the part where the first blade contacts the first hub, and the first blade tip is the first blade far away from the The part of the first blade root, the line between the opposite ends of the first blade tip is the chord line of the first blade tip, and the first blade tip is away from the chord line of the first blade tip The direction of the blade is bent so that the pressure surface of the first blade is located at the first blade tip as an inner concave surface, and the first blade root smoothly transitions to the first blade tip.
上述轴流叶轮在使用时，将多个第一叶片间隔设置于第一轮毂上。第一叶片包括第一叶根与第一叶顶，其中，第一叶根为第一叶片与第一轮毂相接触的部分，第一叶顶为远离第一叶根的部分。第一叶顶向远离第一叶顶的弦线的方向弯曲设置，以使第一叶片的压力面位于第一叶顶的部分为内凹面，能够提高第一叶片的压力面的做功效率。在保证第一叶片做功的同时，降低风对第一叶片的负载，使得第一风叶的功率降低，进而降低轴流叶轮的功率。同时，第一叶根平滑过渡至第一叶顶，能够有效提高第一叶片导风的流畅性，提高送风的舒适度。When the above-mentioned axial flow impeller is in use, a plurality of first blades are arranged on the first hub at intervals. The first blade includes a first blade root and a first blade tip, wherein the first blade root is a part where the first blade contacts the first hub, and the first blade tip is a part away from the first blade root. The first blade tip is bent in a direction away from the chord line of the first blade tip, so that the pressure surface of the first blade located at the first blade tip is a concave surface, which can improve the work efficiency of the pressure surface of the first blade. While ensuring the work of the first blades, the load of the wind on the first blades is reduced, so that the power of the first blades is reduced, thereby reducing the power of the axial flow impeller. At the same time, the first blade root smoothly transitions to the first blade tip, which can effectively improve the smoothness of the first blade's air guide and improve the comfort of air supply.
在其中一个实施例中，所述第一叶片靠近所述第一叶顶部分的相对两端分别形成第一叶尖与第一叶尾，所述第一叶尖外缘的圆角尺寸为R1，所述第一叶尾外缘的圆角尺寸为R2，其中，R2>R1。In one of the embodiments, the opposite ends of the first blade near the first blade tip portion respectively form a first blade tip and a first blade tail, and the rounded size of the outer edge of the first blade tip is R1 , The rounded size of the outer edge of the first blade tail is R2, where R2>R1.
在其中一个实施例中，所述第一叶尖外缘的圆角尺寸R1为2mm～8mm；或In one of the embodiments, the fillet size R1 of the outer edge of the first blade tip is 2 mm to 8 mm; or
所述第一叶尾外缘的圆角尺寸R2为30mm～50mm。The fillet size R2 of the outer edge of the first blade tail is 30mm-50mm.
在其中一个实施例中，所述第一叶尖外缘的圆角尺寸R1为2mm～8mm；In one of the embodiments, the round corner size R1 of the outer edge of the first blade tip is 2 mm to 8 mm;
所述第一叶尾外缘的圆角尺寸R2为30mm～50mm。The fillet size R2 of the outer edge of the first blade tail is 30mm-50mm.
在其中一个实施例中，所述第一叶尾朝向所述第一叶片的压力面的方向弯曲形成弯掠部。In one of the embodiments, the first blade tail is curved toward the pressure surface of the first blade to form a swept portion.
在其中一个实施例中，所述弯掠部相对于所述第一叶顶的切平面之间的夹角β为0°～15°。In one of the embodiments, the included angle β between the swept portion and the tangent plane of the first blade tip is 0°-15°.
在其中一个实施例中，所述第一叶顶与所述第一叶顶弦线之间的最大距离为a，所述第一叶顶弦线的弦长为L2，其中a/L2＝0.03～0.06。In one of the embodiments, the maximum distance between the first blade tip and the first blade tip chord line is a, and the chord length of the first blade tip chord line is L2, where a/L2=0.03 ~0.06.
在其中一个实施例中，所述第一叶根相对于所述第一轮毂的轴线的安装角度为α1，所述第一叶顶相对于所述第一轮毂的轴线的安装角度为α2，其中，α2>α1。In one of the embodiments, the installation angle of the first blade root relative to the axis of the first hub is α1, and the installation angle of the first blade tip relative to the axis of the first hub is α2, where , Α2>α1.
在其中一个实施例中，所述第一叶根相对于所述第一轮毂的轴线的安装角度α1为40°～60°；或In one of the embodiments, the installation angle α1 of the first blade root relative to the axis of the first hub is 40°-60°; or
所述第一叶顶相对于所述第一轮毂的轴线的安装角度α2为60°～75°。The installation angle α2 of the first blade tip relative to the axis of the first hub is 60°-75°.
在其中一个实施例中，所述第一叶根相对于所述第一轮毂的轴线的安装角度α1为40°～60°；In one of the embodiments, the installation angle α1 of the first blade root relative to the axis of the first hub is 40°-60°;
所述第一叶顶相对于所述第一轮毂的轴线的安装角度α2为60°～75°。The installation angle α2 of the first blade tip relative to the axis of the first hub is 60°-75°.
在其中一个实施例中，所述第一叶根相对两端之间的连线为第一叶根的弦线，所述第一叶根弦线的弦长为L1，所述第一叶顶弦线的弦长为L2，其中，L2>L1。In one of the embodiments, the line between opposite ends of the first blade root is the chord line of the first blade root, the chord length of the first blade root chord line is L1, and the first blade tip The chord length of the string is L2, where L2>L1.
在其中一个实施例中，所述第一叶根弦线的弦长L1为40mm～60mm；或In one of the embodiments, the chord length L1 of the first blade root chord line is 40mm-60mm; or
所述第一叶顶弦线的弦长L2为60mm～80mm。The chord length L2 of the first blade tip chord line is 60 mm to 80 mm.
在其中一个实施例中，所述第一叶根弦线的弦长L1为40mm～60mm；In one of the embodiments, the chord length L1 of the first blade root chord line is 40mm-60mm;
所述第一叶顶弦线的弦长L2为60mm～80mm。The chord length L2 of the first blade tip chord line is 60 mm to 80 mm.
在其中一个实施例中，还包括第二风叶，所述第一轮毂的内壁围成一安装腔，所述第二风叶设置于所述安装腔内。In one of the embodiments, it further includes a second wind blade, the inner wall of the first hub encloses an installation cavity, and the second wind blade is arranged in the installation cavity.
在其中一个实施例中，所述第二风叶包括多个第二叶片及第二轮毂，所述多个第二叶片间隔设置于所述第二轮毂上；In one of the embodiments, the second wind blade includes a plurality of second blades and a second hub, and the plurality of second blades are arranged on the second hub at intervals;
其中，所述第二轮毂的直径尺寸D1与所述第二叶片的外径尺寸D2的比值为0.2～0.3；和/或所述第二叶片的外径尺寸D2与所述第一叶片的外径尺寸D3的比值为0.5～0.7。Wherein, the ratio of the diameter D1 of the second hub to the outer diameter D2 of the second blade is 0.2-0.3; and/or the outer diameter D2 of the second blade and the outer diameter of the first blade The ratio of the diameter dimension D3 is 0.5 to 0.7.
在其中一个实施例中，所述第二叶片与所述第二轮毂相接触的部分形成第二叶根，所述第二叶片还具有第二叶顶，所述第二叶顶为远离所述第二叶根的部分，所述第二叶根相对于所述第二轮毂的轴线的安装角度为α3，所述第二叶顶相对于所述第二轮毂的轴线的安装角度为α4，其中，α4>α3。In one of the embodiments, the part of the second blade in contact with the second hub forms a second blade root, the second blade further has a second blade tip, and the second blade tip is away from the For the part of the second blade root, the installation angle of the second blade root relative to the axis of the second hub is α3, and the installation angle of the second blade tip relative to the axis of the second hub is α4, where , Α4>α3.
在其中一个实施例中，所述第二叶根相对于所述第二轮毂的轴线的安装角度α3为30°～50°；和/或In one of the embodiments, the installation angle α3 of the second blade root relative to the axis of the second hub is 30°-50°; and/or
所述第二叶顶相对于所述第二轮毂的轴线的安装角度α4为60°～75°。The installation angle α4 of the second blade tip relative to the axis of the second hub is 60°-75°.
在其中一个实施例中，所述第二叶根相对两端之间的连线为所述第二叶根的弦线，所述第二叶根弦线的弦长为L3，所述第二叶顶相对两端之间的连线为所述第二叶顶的弦线，所述第二叶顶弦线的弦长为L4，其中，L4>L3。In one of the embodiments, the line between the opposite ends of the second blade root is the chord line of the second blade root, the chord length of the second blade root chord is L3, and the second blade root chord has a chord length of L3. The line between the opposite ends of the blade tip is the chord line of the second blade tip, and the chord length of the second blade tip chord line is L4, where L4>L3.
在其中一个实施例中，所述第二叶根弦线的弦长L3为20mm～40mm；或In one of the embodiments, the chord length L3 of the second blade root chord line is 20mm-40mm; or
所述第二叶顶弦线的弦长L4为50mm～70mm。The chord length L4 of the second blade tip chord line is 50mm-70mm.
在其中一个实施例中，所述第二叶根弦线的弦长L3为20mm～40mm；In one of the embodiments, the chord length L3 of the second blade root chord line is 20mm-40mm;
所述第二叶顶弦线的弦长L4为50mm～70mm。The chord length L4 of the second blade tip chord line is 50mm-70mm.
在其中一个实施例中，所述第一风叶与所述第二风叶为一体成型结构。In one of the embodiments, the first wind blade and the second wind blade are integrally formed.
一种风扇，包括：A fan, including:
如上所述的轴流叶轮；及The axial flow impeller as described above; and
转动件，所述转动件用于驱动所述轴流叶轮转动。The rotating member is used to drive the axial flow impeller to rotate.
上述风扇在使用时，将多个第一叶片间隔设置于第一轮毂上。通过转动件驱动轴流叶轮转动，实现风扇的送风。其中，第一叶片包括第一叶根与第一叶顶，第一叶根为第一叶片与第一轮毂相接触的部分，第一叶顶为远离第一叶根的部分。第一叶顶向远离第一叶顶的弦线的方向弯曲设置，以使第一叶片的压力面位于第一叶顶的部分为内凹面，能够提高第一叶片的压力面的做功效率。在保证第一叶片做功的同时，降低风对第一叶片的负载，使得第一风叶的功率降低，进而降低轴流叶轮的功率，使得风扇更加节能。同时，第一叶根平滑过渡至第一叶顶，能够有效提高第一叶片导风的流畅性，提高风扇送风的舒适度。When the above-mentioned fan is in use, a plurality of first blades are arranged on the first hub at intervals. The rotating part drives the axial flow impeller to rotate, so as to realize the air supply of the fan. The first blade includes a first blade root and a first blade tip, the first blade root is the part where the first blade contacts the first hub, and the first blade tip is a part away from the first blade root. The first blade tip is bent in a direction away from the chord line of the first blade tip, so that the pressure surface of the first blade located at the first blade tip is a concave surface, which can improve the work efficiency of the pressure surface of the first blade. While ensuring the work of the first blade, the load of the wind on the first blade is reduced, so that the power of the first blade is reduced, thereby reducing the power of the axial flow impeller, so that the fan is more energy-saving. At the same time, the first blade root smoothly transitions to the first blade tip, which can effectively improve the smoothness of the first blade's air guide and improve the comfort of the fan.
附图说明Description of the drawings
图1为一实施例中的轴流叶轮的主视图；Figure 1 is a front view of an axial flow impeller in an embodiment;
图2为图1所示的轴流叶轮的侧视图；Figure 2 is a side view of the axial flow impeller shown in Figure 1;
图3为图2中A处的放大图；Figure 3 is an enlarged view of A in Figure 2;
图4为图1中第二风叶的主视图；Figure 4 is a front view of the second fan blade in Figure 1;
图5为图4所示的第二风叶的侧视图；Figure 5 is a side view of the second wind blade shown in Figure 4;
图6为图1所示的轴流叶轮的速度云图。Fig. 6 is a velocity cloud diagram of the axial flow impeller shown in Fig. 1.
附图标记说明：Description of reference signs:
10、轴流叶轮，100、第一风叶，110、第一叶片，111、压力面，112、第一叶根，114、第一叶顶，115、第一叶尖，116、第一叶尾，118、弯掠部，120、第一轮毂，200、第二风叶，210、第二叶片，212、第二叶根，220、第二轮毂，300、安装件，310、配合部，320、连接部。10. Axial impeller, 100, first blade, 110, first blade, 111, pressure surface, 112, first blade root, 114, first blade tip, 115, first blade tip, 116, first blade Tail, 118, swept part, 120, first hub, 200, second blade, 210, second blade, 212, second blade root, 220, second hub, 300, mounting part, 310, mating part, 320. Connecting part.
具体实施方式Detailed ways
为使本申请的上述目的、特征和优点能够更加明显易懂，下面结合附图对本申请的具体实施例做详细的说明。在下面的描述中阐述了很多具体细节以便于充分理解本申请。但是本申请能够以很多不同于在此描述的其它方式来实施，本领域技术人员可以在不违背本申请内涵的情况下做类似改进，因此本申请不受下面公开的具体实施的限制。In order to make the above objectives, features and advantages of the present application more obvious and understandable, specific embodiments of the present application will be described in detail below with reference to the accompanying drawings. In the following description, many specific details are set forth in order to fully understand this application. However, this application can be implemented in many other ways different from those described herein, and those skilled in the art can make similar improvements without violating the connotation of this application. Therefore, this application is not limited by the specific implementation disclosed below.
需要说明的是，当元件被称为“固定于”另一个元件，它可以直接在另一个元件上或者也可以存在居中的元件。当一个元件被认为是“连接”另一个元件，它可以是直接连接到另一个元件或者可能同时存在居中元件。本文所使用的术语“垂直的”、“水平的”、“左”、“右”以及类似的表述只是为了说明的目的，并不表示是唯一的实施例。It should be noted that when an element is referred to as being "fixed to" another element, it can be directly on the other element or a central element may also be present. When an element is considered to be "connected" to another element, it can be directly connected to the other element or an intermediate element may be present at the same time. The terms "vertical", "horizontal", "left", "right" and similar expressions used herein are for illustrative purposes only and are not meant to be the only embodiments.
除非另有定义，本文所使用的所有的技术和科学术语与属于本申请的技术领域的技术人员通常理解的含义相同。本文中在本申请的说明书中所使用的术语只是为了描述具体的实施例的目的，不是旨在于限制本申请。以上所述实施例的各技术特征可以进行任意的组合，为使描述简洁，未对上述实施例中的各个技术特征所有可能的组合都进行描述，然而，只要这些技术特征的组合不存在矛盾，都应当认为是本说明书记载的范围。Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by those skilled in the technical field of this application. The terminology used in the specification of the application herein is only for the purpose of describing specific embodiments, and is not intended to limit the application. The technical features of the above-mentioned embodiments can be combined arbitrarily. In order to make the description concise, all possible combinations of the various technical features in the above-mentioned embodiments are not described. However, as long as there is no contradiction in the combination of these technical features, All should be considered as the scope of this specification.
此外，还需要理解的是，在本实施例中，术语“下”、“上”、“前”、“后”、“左”、“右”、“内”、“外”、“顶”、“底”、“一侧”、“另一侧”、“一端”、“另一端”、等所指示的位置关系为基于附图所示的位置关系；“第一”、“第二”等术语，是为了区分不同的结构部件。这些术语仅为了便于描述本申请和简化描述，不能理解为对本申请的限制。In addition, it should be understood that in this embodiment, the terms "down", "upper", "front", "rear", "left", "right", "inner", "outer", "top" The positional relationship indicated by "bottom", "one side", "the other side", "one end", "the other end", etc. are based on the positional relationship shown in the drawings; "first", "second" And other terms are used to distinguish different structural components. These terms are only used to facilitate the description of the application and simplify the description, and should not be construed as limitations on the application.
请参阅图1及图2，一实施例中的轴流叶轮10，至少能够在降低功率的情况下，保证做功，保证送风风量与送风范围，使得轴流叶轮10更加节能。1 and 2, the axial flow impeller 10 in an embodiment can at least guarantee work and air supply air volume and air supply range when the power is reduced, so that the axial flow impeller 10 is more energy-saving.
具体地，轴流叶轮10包括第一风叶100，第一风叶100包括多个第一叶片110及第一 轮毂120，多个第一叶片110间隔设置于第一轮毂120上；第一叶片110包括第一叶根112与第一叶顶114，第一叶根112为第一叶片110与第一轮毂120相接触的部分，第一叶顶114为第一叶片110远离第一叶根112的部分，第一叶顶114的相对两端之间的连线为第一叶顶114的弦线，第一叶顶114向远离第一叶顶114的弦线的方向弯曲设置，以使第一叶片110的压力面111位于第一叶顶114的部分为内凹面，第一叶根112平滑过渡至第一叶顶114。其中，第一叶片110的压力面111为朝向第一风叶100的转动方向的表面。Specifically, the axial flow impeller 10 includes a first fan blade 100, the first fan blade 100 includes a plurality of first blades 110 and a first hub 120, and the plurality of first blades 110 are arranged on the first hub 120 at intervals; the first blades 110 includes a first blade root 112 and a first blade tip 114, the first blade root 112 is the part where the first blade 110 contacts the first hub 120, and the first blade tip 114 is the first blade 110 away from the first blade root 112 The line between the opposite ends of the first blade tip 114 is the chord line of the first blade tip 114, and the first blade tip 114 is bent in a direction away from the chord line of the first blade tip 114, so that the first blade tip 114 The portion where the pressure surface 111 of a blade 110 is located at the first blade tip 114 is an inner concave surface, and the first blade root 112 smoothly transitions to the first blade tip 114. The pressure surface 111 of the first blade 110 is a surface facing the rotation direction of the first blade 100.
上述轴流叶轮10在使用时，将多个第一叶片110间隔设置于第一轮毂120上。其中第一叶片110包括第一叶根112与第一叶顶114，其中，第一叶根112为第一叶片110与第一轮毂120相接触的部分，第一叶顶114为远离第一叶根112的部分。第一叶顶114向远离第一叶顶114的弦线的方向弯曲设置，以使第一叶片110的压力面111位于第一叶顶114的部分为内凹面，能够提高第一叶片110的压力面111的做功效率，能够在保证第一叶片110做功的同时，降低风对第一叶片110的负载，使得第一风叶100的功率降低，进而降低轴流叶轮10的功率。同时，第一叶根112平滑过渡至所述第一叶顶114，进而能够有效提高第一叶片110导风的流畅性，提高送风的舒适度。When the above-mentioned axial flow impeller 10 is in use, a plurality of first blades 110 are arranged on the first hub 120 at intervals. The first blade 110 includes a first blade root 112 and a first blade tip 114, wherein the first blade root 112 is the contact part of the first blade 110 and the first hub 120, and the first blade tip 114 is away from the first blade. The part of the root 112. The first blade tip 114 is bent in a direction away from the chord line of the first blade tip 114, so that the pressure surface 111 of the first blade 110 is located on the first blade tip 114 as a concave surface, which can increase the pressure of the first blade 110 The work efficiency of the surface 111 can reduce the load of the wind on the first blade 110 while ensuring the work of the first blade 110, so that the power of the first blade 100 is reduced, and thus the power of the axial flow impeller 10 is reduced. At the same time, the first blade root 112 smoothly transitions to the first blade tip 114, which can effectively improve the smoothness of the first blade 110 to guide the wind and improve the comfort of air supply.
请一并参阅图3，一实施例中，第一叶根112的相对两端之间的连线为第一叶根112的弦线，第一叶根112向远离第一叶根112的弦线的方向弯曲设置。其中，第一叶根112的弯度与第一叶顶114的弯度可以相同或不相同，第一叶根112平滑过渡至第一叶顶114。另一实施例中，第一叶根112还可以不进行弯曲，第一叶根112平滑过渡至第一叶顶114。Please refer to FIG. 3 together. In one embodiment, the connecting line between the opposite ends of the first blade root 112 is the chord line of the first blade root 112, and the chord line of the first blade root 112 is away from the first blade root 112. The direction of the line is set to bend. The curvature of the first blade root 112 and the curvature of the first blade tip 114 may be the same or different, and the first blade root 112 smoothly transitions to the first blade tip 114. In another embodiment, the first blade root 112 may not be bent, and the first blade root 112 smoothly transitions to the first blade tip 114.
一实施例中，第一叶顶114与第一叶顶114弦线之间的最大距离为a，第一叶顶114弦线的弦长为L2，其中a/L2＝0.03～0.06。当a/L2在0.03～0.06的范围，能够在保证第一叶片110做功的基础上，降低第一叶片110的负载，进而降低第一风叶100的功率，使得第一风叶100在使用过程中更加节能。在相同转速下，若第一叶顶114不弯曲，则会导致第一叶片110的负载增加，进而导致第一风叶100的功率增加，叶片的气动效率低；若第二叶顶的弯曲度过大，则或导致第一叶片110的做功效率低，风量变小，进而导致第一风叶100的效率降低。具体地，a/L2的比值可以为0.03、0.04、0.05或0.06。In one embodiment, the maximum distance between the chord line of the first blade tip 114 and the first blade tip 114 is a, and the chord length of the first blade tip 114 is L2, where a/L2=0.03-0.06. When a/L2 is in the range of 0.03 to 0.06, the load of the first blade 110 can be reduced on the basis of ensuring the work of the first blade 110, thereby reducing the power of the first blade 100, so that the first blade 100 is in use. It is more energy-efficient. At the same rotation speed, if the first blade tip 114 is not bent, the load of the first blade 110 will increase, which in turn will increase the power of the first blade 100, and the aerodynamic efficiency of the blade will be low; if the curvature of the second blade tip is If it is too large, the work efficiency of the first blade 110 may be low, the air volume becomes small, and the efficiency of the first blade 100 may decrease. Specifically, the ratio of a/L2 may be 0.03, 0.04, 0.05, or 0.06.
请参阅图1，一实施例中，第一叶片110靠近第一叶顶114部分的相对两端分别形成第一叶尖115与第一叶尾116，第一叶尖115外缘的圆角尺寸为R1，第一叶尾116外缘的圆角尺寸为R2，其中，R2>R1。将第一叶尖115的外缘设置为较小圆角，同时第一叶尖115位于第一叶片110的前缘，进而可以降低第一叶尖115对进入气流的冲击，减小第一叶尖115的涡流，进而降低噪音的产生。而第一叶尾116的外缘设置为较大圆角，通过较大的圆角设计能够减弱位于第一叶尾116处的尾迹涡流的脱落，进而减弱尾迹涡流对第一 叶尾116处气流流动的影响，能够进一步降低噪音，改善音质。Please refer to FIG. 1, in an embodiment, the opposite ends of the first blade 110 near the first blade tip 114 respectively form a first blade tip 115 and a first blade tail 116, and the rounded size of the outer edge of the first blade tip 115 R1, the rounded size of the outer edge of the first blade tail 116 is R2, where R2>R1. The outer edge of the first blade tip 115 is set to a small rounded corner, and the first blade tip 115 is located at the front edge of the first blade 110, thereby reducing the impact of the first blade tip 115 on the incoming airflow and reducing the first blade tip 115 The eddy current of the tip 115 in turn reduces the generation of noise. The outer edge of the first blade tail 116 is set with a larger rounded corner, and the larger rounded design can reduce the shedding of the wake vortex at the first blade tail 116, thereby reducing the flow of the wake vortex on the first blade tail 116. The influence of this can further reduce noise and improve sound quality.
可选地，第一叶尖115外缘的圆角尺寸R1为2mm～8mm，有效减小第一叶尖115的涡流，进而有效降低噪音。具体地，第一叶尖115外缘的圆角尺寸R1可以为2mm、3mm、4mm、5mm、6mm、7mm或8mm等。进一步地，第一叶尖115外缘的圆角尺寸R1还可以根据第一叶片110的整体尺寸的大小进行调整。例如当第一叶片110的尺寸较大时，可以选择较大的第一叶尖115的圆角尺寸。Optionally, the rounded corner size R1 of the outer edge of the first blade tip 115 is 2 mm to 8 mm, which effectively reduces the eddy current of the first blade tip 115, thereby effectively reducing noise. Specifically, the rounded corner size R1 of the outer edge of the first blade tip 115 may be 2 mm, 3 mm, 4 mm, 5 mm, 6 mm, 7 mm, 8 mm, or the like. Further, the rounded corner size R1 of the outer edge of the first blade tip 115 can also be adjusted according to the overall size of the first blade 110. For example, when the size of the first blade 110 is larger, the rounded size of the first blade tip 115 may be larger.
可选地，第一叶尾116外缘的圆角尺寸R2为30mm～50mm，有效降低尾迹涡流的脱落，进而降低噪音。具体地，第一叶尾116外缘的圆角尺寸R2可以为30mm、40mm或50mm等。进一步地，第一叶尾116外缘的圆角尺寸R2还可以根据第一叶片110的整体尺寸的大小进行调整。例如当第一叶片110的尺寸较大时，可以选择较大的第一叶尾116的圆角尺寸。Optionally, the fillet size R2 of the outer edge of the first blade tail 116 is 30 mm-50 mm, which effectively reduces the shedding of wake vortices and thereby reduces noise. Specifically, the fillet size R2 of the outer edge of the first blade tail 116 may be 30 mm, 40 mm, 50 mm, or the like. Further, the fillet size R2 of the outer edge of the first blade tail 116 can also be adjusted according to the overall size of the first blade 110. For example, when the size of the first blade 110 is larger, the fillet size of the first blade tail 116 may be larger.
请参阅图3，一实施例中，第一叶尾116朝向第一叶片110的压力面111的方向弯曲形成弯掠部118，能够进一步减小尾迹涡流的脱落，增大弯掠部118的做功，进而提高风量。同时弯掠部118可以使第一叶片110上的气流在流出时扩散，增大送风范围。通过弯掠部118还能够有效降低第一叶尾116和相邻第一叶片110的第一叶尖115的流体的干涉，避免造成扰流形成气动异音。Referring to FIG. 3, in an embodiment, the first blade tail 116 is bent toward the pressure surface 111 of the first blade 110 to form a swept portion 118, which can further reduce the shedding of wake vortices and increase the work of the swept portion 118 , And then increase the air volume. At the same time, the swept portion 118 can spread the air flow on the first blade 110 when it flows out, and increase the air supply range. The swept portion 118 can also effectively reduce the fluid interference between the first blade tail 116 and the first blade tip 115 of the adjacent first blade 110, and avoid causing turbulence to form aerodynamic noise.
一实施例中，弯掠部118相对于第一叶顶114的切平面之间的夹角β为0°～15°。能够在保证提高风量的同时，避免功率的明显增大。具体地，弯掠部118相对于第一叶顶114的切平面之间的夹角β可以为0°、5°、10°或15°。其中，第一叶顶114的切平面为第一叶顶114最弯点的切平面。In an embodiment, the angle β between the tangent plane of the swept portion 118 relative to the first blade tip 114 is 0°-15°. It can avoid the obvious increase of power while ensuring the increase of air volume. Specifically, the included angle β between the swept portion 118 and the tangent plane of the first blade tip 114 may be 0°, 5°, 10°, or 15°. The tangent plane of the first blade tip 114 is the tangent plane of the most inflection point of the first blade tip 114.
一实施例中，弯掠部118与第一叶根112之间的高度约占第一叶根112与第一叶顶114之间的距离的三分之一。进而避免弯掠部118过大而影响第一叶片110的做功的能效比。In one embodiment, the height between the swept portion 118 and the first blade root 112 is about one third of the distance between the first blade root 112 and the first blade tip 114. In turn, it is avoided that the swept portion 118 is too large to affect the energy efficiency ratio of the work performed by the first blade 110.
一实施例中，第一叶根112相对于第一轮毂120的轴线的安装角度为α1，第一叶顶114相对于第一轮毂120的轴线的安装角度为α2，其中，α2>α1，能够保证第一叶片110的做功。若α2<α1，则会导致第一叶片110的功率增大，而做功效果却较差，进而导致第一叶片110工作效率降低。同时还会导致第一叶片110的负载增大，进而容易导致第一叶片110发生变形，影响轴流叶轮10的使用使命及使用稳定性。In an embodiment, the installation angle of the first blade root 112 relative to the axis of the first hub 120 is α1, and the installation angle of the first blade tip 114 relative to the axis of the first hub 120 is α2, where α2>α1 can be Ensure the work of the first blade 110. If α2<α1, the power of the first blade 110 will increase, but the work effect will be poor, and the work efficiency of the first blade 110 will decrease. At the same time, the load of the first blade 110 will increase, which will easily cause the first blade 110 to deform, which will affect the mission and stability of the axial flow impeller 10.
可选地，第一叶根112相对于第一轮毂120的轴线的安装角度α1为40°～60°，进而能够保证第一叶片110的做功，且避免功率的增大。具体地，安装角度α1可以为40°、45°、50°、55°或60°。Optionally, the installation angle α1 of the first blade root 112 with respect to the axis of the first hub 120 is 40°-60°, thereby ensuring the work of the first blade 110 and avoiding an increase in power. Specifically, the installation angle α1 may be 40°, 45°, 50°, 55°, or 60°.
可选地，第一叶顶114相对于第一轮毂120的轴线的安装角度α2为60°～75°，能 够保证第一叶片110的做功，且避免功率的增大。具体地，安装角度α2可以为60°、65°、70°或75°。Optionally, the installation angle α2 of the first blade tip 114 relative to the axis of the first hub 120 is 60°˜75°, which can ensure the work of the first blade 110 and avoid an increase in power. Specifically, the installation angle α2 may be 60°, 65°, 70°, or 75°.
一实施例中，第一叶根112弦线的弦长为L1，第一叶顶114弦线的弦长为L2，其中，L2>L1。通过设置L2>L1能够进一步保证第一叶片110的做功，且避免功率的增大。In one embodiment, the chord length of the first blade root 112 is L1, and the chord length of the first blade tip 114 is L2, where L2>L1. By setting L2>L1, the work done by the first blade 110 can be further ensured, and the increase in power can be avoided.
可选地，第一叶根112弦线的弦长L1为40mm～60mm，进而能够有效保证第一叶片110的做功面积，避免影响第一叶片110的送分风量。Optionally, the chord length L1 of the chord line of the first blade root 112 is 40 mm-60 mm, which can effectively ensure the work area of the first blade 110 and avoid affecting the air distribution volume of the first blade 110.
可选地，第一叶顶114弦线的弦长L2为60mm～80mm，能够进一步有效保证第一叶片110的做功面积，避免影响第一叶片110的送风风量。在其他实施例中，第一叶根112弦线的弦长L1和第一叶顶114弦线的弦长L2还可以根据第一叶片110的整体尺寸的增大而适当的增大，或者根据第一叶片110的整体尺寸的减小而适当减小。Optionally, the chord length L2 of the chord line of the first blade tip 114 is 60 mm to 80 mm, which can further effectively ensure the work area of the first blade 110 and avoid affecting the air supply volume of the first blade 110. In other embodiments, the chord length L1 of the chord line of the first blade root 112 and the chord length L2 of the chord line of the first blade tip 114 may also be appropriately increased according to the increase in the overall size of the first blade 110, or according to The overall size of the first blade 110 is reduced appropriately.
请一并参阅图1及图4，一实施例中，轴流叶轮10还包括第二风叶200，第一轮毂120的内壁围成一安装腔，第二风叶200设置于安装腔内。一方面通过设置第二风叶200能够进一步加强第一风叶100的结构，使得轴流叶轮10的结构更加稳定。另一方面，通过设置第二风叶200能够进一步增加轴流叶轮10的风量及送风范围。1 and 4 together, in one embodiment, the axial flow impeller 10 further includes a second fan blade 200, the inner wall of the first hub 120 encloses an installation cavity, and the second fan blade 200 is disposed in the installation cavity. On the one hand, the structure of the first fan blade 100 can be further strengthened by arranging the second fan blade 200, so that the structure of the axial flow impeller 10 is more stable. On the other hand, by providing the second fan blade 200, the air volume and the air blowing range of the axial flow impeller 10 can be further increased.
具体地，第二风叶200包括多个第二叶片210及第二轮毂220，多个第二叶片210间隔设置于第二轮毂220上。通过第二轮毂220带动第二叶片210转动，进而实现第二风叶200的送风。Specifically, the second wind blade 200 includes a plurality of second blades 210 and a second hub 220, and the plurality of second blades 210 are arranged on the second hub 220 at intervals. The second blade 210 is driven to rotate by the second hub 220, so as to realize the air supply of the second blade 200.
在本实施例中，第一风叶100与第二风叶200为一体成型结构。进而第二叶片210远离第二轮毂220的一侧边固定于第一轮毂120上，其中，第二轮毂220用于连接转动件。当第二风叶200转动时，能够进一步带动第一风叶100转动，实现第一风叶100与第二风叶200的同时转动。具体地，第一风叶100与第二风叶200一体注塑成型，使得轴流叶轮10的结构更加稳定。In this embodiment, the first fan blade 100 and the second fan blade 200 are integrally formed. Furthermore, the side of the second blade 210 away from the second hub 220 is fixed on the first hub 120, wherein the second hub 220 is used to connect the rotating member. When the second fan blade 200 rotates, the first fan blade 100 can be further driven to rotate, so that the first fan blade 100 and the second fan blade 200 can rotate at the same time. Specifically, the first fan blade 100 and the second fan blade 200 are integrally injection molded, so that the structure of the axial flow impeller 10 is more stable.
在本实施例中，第一叶片110的数量大于或等于第二叶片210的数量。由于第一风叶100的能效比相比于第二风叶200的能效比较大，进而将第一叶片110的数量设置于大于或等于第二叶片210的数量，能够有效提高轴流叶轮10的整体做功的能效比，降低功率的消耗。In this embodiment, the number of the first blades 110 is greater than or equal to the number of the second blades 210. Since the energy efficiency ratio of the first blade 100 is greater than that of the second blade 200, the number of the first blades 110 is set to be greater than or equal to the number of the second blades 210, which can effectively improve the axial flow impeller 10 The energy efficiency ratio of the overall work reduces power consumption.
具体地，第一叶片110与第二叶片210的数量均为奇数个。进而避免叶片之间对称设置，导致轴流叶轮10在转动的过程中，第一叶片110与第二叶片210受到的离心力、风阻力等对称分布，进而导致轴流叶轮10易发生变形，而采用非对称分布的形成，不同方向上的力能够相互抵消，减小对第一风叶100与第二风叶200上的受力形变。Specifically, the numbers of the first blades 110 and the second blades 210 are both odd numbers. Furthermore, it is avoided that the blades are symmetrically arranged, resulting in the symmetrical distribution of centrifugal force, wind resistance, etc. received by the first blade 110 and the second blade 210 during the rotation of the axial flow impeller 10, thereby causing the axial flow impeller 10 to be easily deformed. With the formation of asymmetrical distribution, the forces in different directions can cancel each other, reducing the force deformation on the first blade 100 and the second blade 200.
在本实施例中，第一叶片110的数量为七个。第二叶片210的数量为五个。当然，第 一叶片110的数量还可以为三个、五个、九个等数目个。第二叶片210的数量还可以为三个、七个等其他数目个。In this embodiment, the number of first blades 110 is seven. The number of second blades 210 is five. Of course, the number of the first blades 110 can also be three, five, nine, etc. The number of the second blades 210 can also be three, seven, or other numbers.
请再次参阅图1，在本实施例中，第二叶片210的外径尺寸D2与第一叶片110的外径尺寸D3的比值为0.5～0.7。轴流叶轮10的第二风叶200为主要做功部件，而第二风叶200的做功相对较少。通过控制第二叶片210与第一叶片110的外径比值，进而能够控制第二叶片210与第一叶片110的做功面积。一般情况下，若D2/D3的比值较大时，即第二叶片210的外径尺寸较大，第一叶片110的做功面积就会减少。若D2/D3的比值较小时，第二叶片210的外径尺寸较小，第一叶片110的做功面积大，但会造成轴流叶轮10整体功率增加。将D2/D3控制在0.5～0.7，能够有效保证做功，且避免功率的增大。Please refer to FIG. 1 again. In this embodiment, the ratio of the outer diameter D2 of the second blade 210 to the outer diameter D3 of the first blade 110 is 0.5-0.7. The second wind blade 200 of the axial flow impeller 10 is the main work component, while the second wind blade 200 does relatively little work. By controlling the ratio of the outer diameters of the second blade 210 to the first blade 110, the work area of the second blade 210 and the first blade 110 can be controlled. Generally, if the ratio of D2/D3 is larger, that is, the outer diameter of the second blade 210 is larger, the work area of the first blade 110 will be reduced. If the ratio of D2/D3 is small, the outer diameter of the second blade 210 is small, and the work area of the first blade 110 is large, but the overall power of the axial flow impeller 10 will increase. Controlling D2/D3 at 0.5～0.7 can effectively ensure the work and avoid the increase of power.
具体地，第一轮毂120的外径尺寸与第一叶片110的外径尺寸D3的比值可以为0.55～0.65。Specifically, the ratio of the outer diameter size of the first hub 120 to the outer diameter size D3 of the first blade 110 may be 0.55 to 0.65.
在本实施例中，第一轮毂120的壁厚为2mm～6mm。第一轮毂120为第一叶片110与第二叶片210连接的桥梁。通过控制第一轮毂120的壁厚能够保持第一叶片110与第二叶片210的连接强度，提高结构的稳定性，同时，提高轴流叶轮10整体的协调。具体地，第一轮毂120的壁厚为4mm。In this embodiment, the wall thickness of the first hub 120 is 2 mm to 6 mm. The first hub 120 is a bridge connecting the first blade 110 and the second blade 210. By controlling the wall thickness of the first hub 120, the connection strength of the first blade 110 and the second blade 210 can be maintained, the stability of the structure can be improved, and the overall coordination of the axial flow impeller 10 can be improved. Specifically, the wall thickness of the first hub 120 is 4 mm.
可选地，第二轮毂220的直径尺寸D1与第二叶片210的外径尺寸D2的比值为0.2～0.3。一方面保证第二轮毂220能够有效连接转动件，另一面通过控制第二轮毂220与第二叶片210的外径尺寸的比值，能够有效控制第二叶片210的做功与功率。Optionally, the ratio of the diameter D1 of the second hub 220 to the outer diameter D2 of the second blade 210 is 0.2-0.3. On the one hand, it is ensured that the second hub 220 can be effectively connected to the rotating parts, and on the other hand, by controlling the ratio of the outer diameter of the second hub 220 to the second blade 210, the work and power of the second blade 210 can be effectively controlled.
请参阅图4及图5，一实施例中，第二叶片210与第二轮毂220相接触的部分形成第二叶根212，第二叶片210还具有第二叶顶214，第二叶顶214为第二叶片210远离第二叶根212的部分，第二叶根212相对于第二轮毂220的轴线的安装角度为α3，第二叶顶214相对于第二轮毂220的轴线的安装角度为α4，其中，α4>α3。在保证第二叶片210的做功效率的同时，避免导致第二叶片210的功率消耗增大。4 and 5, in one embodiment, the part where the second blade 210 is in contact with the second hub 220 forms a second blade root 212, and the second blade 210 further has a second blade tip 214, and a second blade tip 214 Is the part of the second blade 210 away from the second blade root 212, the installation angle of the second blade root 212 relative to the axis of the second hub 220 is α3, and the installation angle of the second blade tip 214 relative to the axis of the second hub 220 is α4, where α4>α3. While ensuring the work efficiency of the second blade 210, the power consumption of the second blade 210 is prevented from increasing.
可选地，第二叶根212相对于第二轮毂220的轴线的安装角度α3为30°～50°。进而能够保证第二叶片210的做功，且避免功率的增大。具体地，安装角度α3可以为30°、35°、40°、45°或50°。Optionally, the installation angle α3 of the second blade root 212 relative to the axis of the second hub 220 is 30°-50°. In turn, the work of the second blade 210 can be ensured, and the increase in power can be avoided. Specifically, the installation angle α3 may be 30°, 35°, 40°, 45°, or 50°.
可选地，第二叶顶214相对于第二轮毂220的轴线的安装角度α4为60°～75°。能够保证第二叶片210的做功，且避免功率的增大。具体地，安装角度α4可以为60°、65°、70°或75°。Optionally, the installation angle α4 of the second blade tip 214 relative to the axis of the second hub 220 is 60°˜75°. It can ensure the work of the second blade 210 and avoid the increase of power. Specifically, the installation angle α4 may be 60°, 65°, 70°, or 75°.
一实施例中，第二叶根212相对两端之间的连线为第二叶根212的弦线，第二叶根212弦线的弦长为L3，第二叶顶214相对两端之间的连线为第二叶顶214的弦线，第二叶顶 214弦线的弦长为L4，其中，L4>L3。通过设置L4>L3能够有效降低第二叶片210功率的消耗，且保证一定的做功，进而提高轴流叶轮10的能效比。In one embodiment, the line between the opposite ends of the second blade root 212 is the chord line of the second blade root 212, the chord length of the second blade root 212 is L3, and the second blade tip 214 has a chord length of L3. The connecting line between is the chord line of the second blade tip 214, and the chord length of the second blade tip 214 is L4, where L4>L3. By setting L4>L3, the power consumption of the second blade 210 can be effectively reduced, and a certain amount of work can be ensured, thereby improving the energy efficiency ratio of the axial flow impeller 10.
可选地，第二叶根212弦线的弦长L3为20mm～40mm，能够进一步有效降低第二叶片210功率的消耗，且保证一定的做功，进而提高轴流叶轮10的能效比。Optionally, the chord length L3 of the chord line of the second blade root 212 is 20 mm-40 mm, which can further effectively reduce the power consumption of the second blade 210 and ensure a certain amount of work, thereby improving the energy efficiency ratio of the axial flow impeller 10.
可选地，第二叶顶214弦线的弦长L4为50mm～70mm，能够进一步有效降低第二叶片210功率的消耗，且保证一定的做功，进而提高轴流叶轮10的能效比。在其他实施例中，第二叶根212弦线的弦长与第二叶顶214弦线的弦长还可以根据第二风叶200的整体尺寸的增大而适当增大，或者根据第二风叶200的整体的尺寸的减小而适当减小。Optionally, the chord length L4 of the chord line of the second blade tip 214 is 50 mm to 70 mm, which can further effectively reduce the power consumption of the second blade 210 and ensure a certain amount of work, thereby improving the energy efficiency ratio of the axial flow impeller 10. In other embodiments, the chord length of the chord line of the second blade root 212 and the chord length of the second blade tip 214 may also be appropriately increased according to the increase in the overall size of the second blade 200, or according to the second blade The overall size of the wind blade 200 is reduced appropriately.
在本实施例中，第二叶片210整体叶型细长，且第二叶片210的叶尖部分仿雨燕翅膀，细长圆润，进而能够在保证风量的同时，降低第二风叶200功率，进而降低轴流叶轮10的功率，提高轴流叶轮10的能效比。In this embodiment, the overall shape of the second blade 210 is slender, and the tip part of the second blade 210 resembles a swift wing, slender and round, which can reduce the power of the second blade 200 while ensuring the air volume, thereby reducing the power of the second blade 200. The power of the axial flow impeller 10 is reduced, and the energy efficiency ratio of the axial flow impeller 10 is improved.
请参阅图6，上述实施例中轴流叶轮10在使用时，送风范围广，风在一定位置交汇后向外扩散，风场更广，风量更大，风感更柔和舒适。同时，上述实施例中轴流叶轮10能有效降低高速旋转时的“嗡嗡声”，改善音质。Please refer to FIG. 6, when the axial flow impeller 10 in the above embodiment is in use, the air supply range is wide, and the wind spreads outward after meeting at a certain position, the wind field is wider, the air volume is larger, and the wind feel is softer and more comfortable. At the same time, the axial flow impeller 10 in the above embodiment can effectively reduce the "humming" during high-speed rotation and improve the sound quality.
上述实施例中的轴流叶轮10与传统的设置有五个叶片的风机的性能对比数据如下表所示：The performance comparison data of the axial flow impeller 10 in the above-mentioned embodiment and the traditional five-blade fan is shown in the following table:
风叶Wind leaf 风量(m3/min)Air volume (m3/min) 噪音(dB)Noise (dB) 功率(W)Power (W)
传统五个叶片的风机Traditional five-blade fan 2828 5858 2828
本申请中的轴流叶轮10 Axial flow impeller 10 in this application 3030 5757 23twenty three
从上述表格中的测试数据可以看出，轴流叶轮10在整体性能上有明显提升，其风量提升2个风量，噪音降低1dB，功率减小5W，轴流叶轮10的整体能效比增大。It can be seen from the test data in the above table that the overall performance of the axial flow impeller 10 has been significantly improved. Its air volume has been increased by two air volumes, the noise has been reduced by 1 dB, the power has been reduced by 5 W, and the overall energy efficiency ratio of the axial flow impeller 10 has increased.
一实施例中的风扇包括上述任一实施例中的轴流叶轮10。具体地，风扇还包括转动件，转动件用于驱动轴流叶轮10转动。进一步地，转动件设置于第二轮毂220上。其中转动件为电机。The fan in one embodiment includes the axial flow impeller 10 in any of the above embodiments. Specifically, the fan further includes a rotating member for driving the axial flow impeller 10 to rotate. Further, the rotating member is arranged on the second hub 220. The rotating part is a motor.
请参阅图1，一实施例中，轴流叶轮10还包括安装件300，安装件300设置于第二轮毂220内，转动件安装于安装件300上。通过设置安装件300能够方便转动件的安装，进而方便通过转动件实现轴流叶轮10转动。Please refer to FIG. 1, in an embodiment, the axial flow impeller 10 further includes a mounting member 300, the mounting member 300 is disposed in the second hub 220, and the rotating member is mounted on the mounting member 300. The installation of the mounting member 300 can facilitate the installation of the rotating member, thereby facilitating the rotation of the axial flow impeller 10 through the rotating member.
具体地，安装件300包括配合部310及连接部320，配合部310通过连接部320设置于第二轮毂220上。配合部310用于与转动件相配合。进一步地，配合部310通过连接部320一体成型于第二轮毂220的内壁上，能够提高安装件300设置于第二轮毂220的稳定性，进而提高转动件安装于轴流叶轮10的稳定性。Specifically, the mounting member 300 includes a mating part 310 and a connecting part 320, and the mating part 310 is disposed on the second hub 220 through the connecting part 320. The mating part 310 is used for mating with the rotating member. Further, the mating portion 310 is integrally formed on the inner wall of the second hub 220 through the connecting portion 320, which can improve the stability of the mounting member 300 on the second hub 220, thereby improving the stability of the rotating member on the axial flow impeller 10.
在本实施例中，风扇为落地式循环扇。在其他实施例中，风扇还可以为其他类型风扇。In this embodiment, the fan is a floor-standing circulation fan. In other embodiments, the fan may also be other types of fans.
以上所述实施例仅表达了本申请的几种实施例，其描述较为具体和详细，但并不能因此而理解为对申请专利范围的限制。应当指出的是，对于本领域的普通技术人员来说，在不脱离本申请构思的前提下，还可以做出若干变形和改进，这些都属于本申请的保护范围。因此，本申请专利的保护范围应以所附权利要求为准。The above-mentioned embodiments only express a few embodiments of the present application, and the description is relatively specific and detailed, but it should not be understood as a limitation on the scope of the patent application. It should be pointed out that for those of ordinary skill in the art, without departing from the concept of this application, several modifications and improvements can be made, and these all fall within the protection scope of this application. Therefore, the scope of protection of the patent of this application shall be subject to the appended claims.

Claims (22)

  1. 一种轴流叶轮，其特征在于，包括第一风叶，所述第一风叶包括多个第一叶片及第一轮毂，所述多个第一叶片间隔设置于所述第一轮毂上；所述第一叶片包括第一叶根与第一叶顶，所述第一叶根为所述第一叶片与所述第一轮毂相接触的部分，所述第一叶顶为所述第一叶片远离所述第一叶根的部分，所述第一叶顶的相对两端之间的连线为所述第一叶顶的弦线，所述第一叶顶向远离所述第一叶顶的弦线的方向弯曲设置，以使所述第一叶片的压力面位于所述第一叶顶的部分为内凹面，所述第一叶根平滑过渡至所述第一叶顶。An axial flow impeller, characterized by comprising a first wind blade, the first wind blade comprising a plurality of first blades and a first hub, and the plurality of first blades are arranged on the first hub at intervals; The first blade includes a first blade root and a first blade tip, the first blade root is the contact part of the first blade and the first hub, and the first blade tip is the first blade tip. The part of the blade away from the first blade root, the line between the opposite ends of the first blade tip is the chord line of the first blade tip, and the first blade tip is away from the first blade The direction of the chord line of the top is curved and arranged, so that the pressure surface of the first blade is located at the first blade tip as an inner concave surface, and the first blade root smoothly transitions to the first blade tip.
  2. 根据权利要求1所述的轴流叶轮，其特征在于，所述第一叶片靠近所述第一叶顶部分的相对两端分别形成第一叶尖与第一叶尾，所述第一叶尖外缘的圆角尺寸为R1，所述第一叶尾外缘的圆角尺寸为R2，其中，R2>R1。The axial flow impeller according to claim 1, wherein the opposite ends of the first blade near the first blade tip portion respectively form a first blade tip and a first blade tail, and the first blade tip The rounded size of the outer edge is R1, and the rounded size of the outer edge of the first blade tail is R2, where R2>R1.
  3. 根据权利要求2所述的轴流叶轮，其特征在于，所述第一叶尖外缘的圆角尺寸R1为2mm～8mm；或The axial flow impeller according to claim 2, wherein the rounded size R1 of the outer edge of the first blade tip is 2mm-8mm; or
    所述第一叶尾外缘的圆角尺寸R2为30mm～50mm。The fillet size R2 of the outer edge of the first blade tail is 30mm-50mm.
  4. 根据权利要求2所述的轴流叶轮，其特征在于，所述第一叶尖外缘的圆角尺寸R1为2mm～8mm；The axial flow impeller according to claim 2, wherein the rounded corner size R1 of the outer edge of the first blade tip is 2 mm to 8 mm;
    所述第一叶尾外缘的圆角尺寸R2为30mm～50mm。The fillet size R2 of the outer edge of the first blade tail is 30mm-50mm.
  5. 根据权利要求2-4任一项所述的轴流叶轮，其特征在于，所述第一叶尾朝向所述第一叶片的压力面的方向弯曲形成弯掠部。The axial flow impeller according to any one of claims 2 to 4, wherein the first blade tail is curved toward the pressure surface of the first blade to form a swept portion.
  6. 根据权利要求5所述的轴流叶轮，其特征在于，所述弯掠部相对于所述第一叶顶的切平面之间的夹角β为0°～15°。The axial flow impeller according to claim 5, wherein the angle β between the tangent plane of the swept portion and the first blade tip is 0°-15°.
  7. 根据权利要求1-4任一项所述的轴流叶轮，其特征在于，所述第一叶顶与所述第一叶顶弦线之间的最大距离为a，所述第一叶顶弦线的弦长为L2，其中a/L2＝0.03～0.06。The axial flow impeller according to any one of claims 1 to 4, wherein the maximum distance between the first blade tip and the first blade tip chord line is a, and the first blade tip chord The chord length of the line is L2, where a/L2=0.03～0.06.
  8. 根据权利要求7所述的轴流叶轮，其特征在于，所述第一叶根相对于所述第一轮毂的轴线的安装角度为α1，所述第一叶顶相对于所述第一轮毂的轴线的安装角度为α2，其中，α2>α1。The axial flow impeller according to claim 7, wherein the installation angle of the first blade root relative to the axis of the first hub is α1, and the first blade tip relative to the first hub The installation angle of the axis is α2, where α2>α1.
  9. 根据权利要求8所述的轴流叶轮，其特征在于，所述第一叶根相对于所述第一轮毂的轴线的安装角度α1为40°～60°；或The axial flow impeller according to claim 8, wherein the installation angle α1 of the first blade root relative to the axis of the first hub is 40°-60°; or
    所述第一叶顶相对于所述第一轮毂的轴线的安装角度α2为60°～75°。The installation angle α2 of the first blade tip relative to the axis of the first hub is 60°-75°.
  10. 根据权利要求8所述的轴流叶轮，其特征在于，所述第一叶根相对于所述第一轮 毂的轴线的安装角度α1为40°～60°；The axial flow impeller according to claim 8, wherein the installation angle α1 of the first blade root relative to the axis of the first hub is 40°-60°;
    所述第一叶顶相对于所述第一轮毂的轴线的安装角度α2为60°～75°。The installation angle α2 of the first blade tip relative to the axis of the first hub is 60°-75°.
  11. 根据权利要求1-4任一项所述的轴流叶轮，其特征在于，所述第一叶根相对两端之间的连线为第一叶根的弦线，所述第一叶根弦线的弦长为L1，所述第一叶顶弦线的弦长为L2，其中，L2>L1。The axial flow impeller according to any one of claims 1-4, wherein the connecting line between opposite ends of the first blade root is a chord line of the first blade root, and the first blade root chord The chord length of the wire is L1, and the chord length of the first blade tip chord is L2, where L2>L1.
  12. 根据权利要求8所述的轴流叶轮，其特征在于，所述第一叶根弦线的弦长L1为40mm～60mm；和/或The axial flow impeller according to claim 8, wherein the chord length L1 of the chord line of the first blade root is 40mm-60mm; and/or
    所述第一叶顶弦线的弦长L2为60mm～80mm。The chord length L2 of the first blade tip chord line is 60 mm to 80 mm.
  13. 根据权利要求1-4任一项所述的轴流叶轮，其特征在于，还包括第二风叶，所述第一轮毂的内壁围成一安装腔，所述第二风叶设置于所述安装腔内。The axial flow impeller according to any one of claims 1-4, further comprising a second wind blade, the inner wall of the first hub encloses an installation cavity, and the second wind blade is arranged in the In the installation cavity.
  14. 根据权利要求13所述的轴流叶轮，其特征在于，所述第二风叶包括多个第二叶片及第二轮毂，所述多个第二叶片间隔设置于所述第二轮毂上；The axial flow impeller according to claim 13, wherein the second wind blade comprises a plurality of second blades and a second hub, and the plurality of second blades are arranged on the second hub at intervals;
    其中，所述第二轮毂的直径尺寸D1与所述第二叶片的外径尺寸D2的比值为0.2～0.3；和/或所述第二叶片的外径尺寸D2与所述第一叶片的外径尺寸D3的比值为0.5～0.7。Wherein, the ratio of the diameter D1 of the second hub to the outer diameter D2 of the second blade is 0.2-0.3; and/or the outer diameter D2 of the second blade and the outer diameter of the first blade The ratio of the diameter dimension D3 is 0.5 to 0.7.
  15. 根据权利要求14所述的轴流叶轮，其特征在于，所述第二叶片与所述第二轮毂相接触的部分形成第二叶根，所述第二叶片还具有第二叶顶，所述第二叶顶为远离所述第二叶根的部分，所述第二叶根相对于所述第二轮毂的轴线的安装角度为α3，所述第二叶顶相对于所述第二轮毂的轴线的安装角度为α4，其中，α4>α3。The axial flow impeller according to claim 14, wherein the part of the second blade in contact with the second hub forms a second blade root, the second blade further has a second blade tip, and The second blade tip is the part away from the second blade root, the installation angle of the second blade root relative to the axis of the second hub is α3, and the second blade tip relative to the second hub The installation angle of the axis is α4, where α4>α3.
  16. 根据权利要求15所述的轴流叶轮，其特征在于，所述第二叶根相对于所述第二轮毂的轴线的安装角度α3为30°～50°；或The axial flow impeller according to claim 15, wherein the installation angle α3 of the second blade root relative to the axis of the second hub is 30°-50°; or
    所述第二叶顶相对于所述第二轮毂的轴线的安装角度α4为60°～75°。The installation angle α4 of the second blade tip relative to the axis of the second hub is 60°-75°.
  17. 根据权利要求15所述的轴流叶轮，其特征在于，所述第二叶根相对于所述第二轮毂的轴线的安装角度α3为30°～50°；The axial flow impeller according to claim 15, wherein the installation angle α3 of the second blade root relative to the axis of the second hub is 30°-50°;
    所述第二叶顶相对于所述第二轮毂的轴线的安装角度α4为60°～75°。The installation angle α4 of the second blade tip relative to the axis of the second hub is 60°-75°.
  18. 根据权利要求15所述的轴流叶轮，其特征在于，所述第二叶根相对两端之间的连线为所述第二叶根的弦线，所述第二叶根弦线的弦长为L3，所述第二叶顶相对两端之间的连线为所述第二叶顶的弦线，所述第二叶顶弦线的弦长为L4，其中，L4>L3。The axial flow impeller according to claim 15, wherein the connecting line between opposite ends of the second blade root is the chord line of the second blade root, and the chord line of the second blade root The length is L3, the line between opposite ends of the second blade tip is the chord line of the second blade tip, and the chord length of the second blade tip chord line is L4, where L4>L3.
  19. 根据权利要求18所述的轴流叶轮，其特征在于，所述第二叶根弦线的弦长L3为20mm～40mm；或The axial flow impeller according to claim 18, wherein the chord length L3 of the second blade root chord line is 20mm-40mm; or
    所述第二叶顶弦线的弦长L4为50mm～70mm。The chord length L4 of the second blade tip chord line is 50mm-70mm.
  20. 根据权利要求18所述的轴流叶轮，其特征在于，所述第二叶根弦线的弦长L3为 20mm～40mm；The axial flow impeller according to claim 18, wherein the chord length L3 of the second blade root chord line is 20mm-40mm;
    所述第二叶顶弦线的弦长L4为50mm～70mm。The chord length L4 of the second blade tip chord line is 50mm-70mm.
  21. 根据权利要求13所述的轴流叶轮，其特征在于，所述第一风叶与所述第二风叶为一体成型结构。The axial flow impeller according to claim 13, wherein the first fan blade and the second fan blade are integrally formed.
  22. 一种风扇，其特征在于，包括：A fan, characterized in that it comprises:
    如权利要求1-21任一项所述的轴流叶轮；及The axial flow impeller according to any one of claims 1-21; and
    转动件，所述转动件用于驱动所述轴流叶轮转动。The rotating member is used to drive the axial flow impeller to rotate.
PCT/CN2020/098689 2019-09-30 2020-06-29 Fan and axial-flow impeller WO2021063050A1 (en)

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