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WO2018126745A1 - 叶片、叶轮及风机 - Google Patents

叶片、叶轮及风机 Download PDF

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Publication number
WO2018126745A1
WO2018126745A1 PCT/CN2017/103960 CN2017103960W WO2018126745A1 WO 2018126745 A1 WO2018126745 A1 WO 2018126745A1 CN 2017103960 W CN2017103960 W CN 2017103960W WO 2018126745 A1 WO2018126745 A1 WO 2018126745A1
Authority
WO
WIPO (PCT)
Prior art keywords
blade
ridge structure
edge
impeller
radially
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2017/103960
Other languages
English (en)
French (fr)
Inventor
曹锋
邹建煌
刘中杰
龙斌华
刘浩
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Gree Electric Appliances Inc of Zhuhai
Original Assignee
Gree Electric Appliances Inc of Zhuhai
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Gree Electric Appliances Inc of Zhuhai filed Critical Gree Electric Appliances Inc of Zhuhai
Priority to US16/471,074 priority Critical patent/US11078921B2/en
Priority to EP17890274.8A priority patent/EP3567258A4/en
Priority to JP2019533011A priority patent/JP6771672B2/ja
Publication of WO2018126745A1 publication Critical patent/WO2018126745A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • 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
    • 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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/164—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of an axial flow wheel
    • 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
    • F04D29/326—Rotors specially for elastic fluids for axial flow pumps for axial flow fans comprising a rotating shroud
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/304—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the trailing edge of a rotor blade
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/305—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the pressure side of a rotor blade
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/306—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the suction side of a rotor blade

Definitions

  • the present invention relates to the field of wind turbines, and more particularly to a blade, an impeller and a fan.
  • a blade is provided.
  • a blade having a trailing edge provided with at least one concave arc, at least one end of the at least one concave arc being located between a radially outer edge and a radially inner edge of the blade, on the blade At least one ridge structure projecting from the pressure of the vane toward the suction side of the vane is provided.
  • one end of the ridge structure meets at the end of the concave arc and the other end meets at the leading edge of the blade.
  • two end points of each of the concave arcs are correspondingly disposed with one of the ridge structures.
  • the blade is provided with a plurality of ridge structures spaced apart from the radially inner edge of the blade toward the radially outer edge, and the maximum height of the ridge structure is directed by the radially inner edge of the blade The direction of the radially outer edge gradually decreases.
  • the trailing edge of the blade is provided with a concave arc
  • the at least one ridge structure protruding from the pressure of the blade toward the suction surface of the blade includes a radially inner edge adjacent to the blade a first ridge structure disposed and a first portion disposed adjacent to a radial outer edge of the blade a second ridge structure, one end of the first ridge structure meets at an end of the concave arc near a radially inner edge of the blade, and the second ridge structure meets the concave arc Near the end of the radial outer edge of the blade.
  • the first ridge structure has a maximum height of W1
  • the second ridge structure has a maximum height of W2, and in the radial direction, a distance between the radially inner edge of the blade and the radially outer edge Is L;
  • W2 k2*L, the coefficient k2 ranges from 0.021 to 0.031.
  • the ridge structure has a circular arc shape.
  • the trailing edge of the blade is provided with a concave arc
  • the at least one ridge structure protruding from the pressure of the blade toward the suction surface of the blade includes a radially inner edge adjacent to the blade a first ridge structure and a second ridge structure disposed adjacent to a radially outer edge of the blade, one end of the first ridge structure intersecting the concave arc in a radial direction of the blade
  • the second ridge structure meets at the end of the concave arc near the radially outer edge of the blade, and the radius of the arc of the first ridge structure in the circumferential direction is R2
  • the radius of the arc of the second ridge structure in the circumferential direction is R3, and the radius of the radially inner edge of the blade is R1;
  • R3 k4 * R1, and the coefficient k4 ranges from 1.95 to 2.05.
  • the center of the ridge structure coincides with the center of the radially inner edge of the blade.
  • the trailing edge of the blade is provided with a concave arc, in the five elementary stages in which the blade is evenly distributed from its radially inner edge to the radially outer edge,
  • the cascade consistency is 0.84 to 0.86, 0.77 to 0.79, 0.54 to 0.56, 0.57 to 0.59, 0.51 to 0.53, and/or
  • the installation angle is 30.5 to 32.5, 24.5 to 26.5, 19.5 to 21.5, 15.5 to 17.5, 13.0 to 15.0, and/or
  • the front bending angle is 0°, 1° to 3°, 7° to 9°, 9° to 11°, and 17° to 19°.
  • the ridge structure has a pointed structure, and the pointed structure and the suction surface and the pressure surface of the blade are connected by a smooth curved transition.
  • the invention provides an impeller.
  • An impeller comprising a blade as described above.
  • the impeller includes a plurality of the blades arranged in the circumferential direction, and adjacent blades have an angle between them, wherein at least one of the included angles is different from the other angles.
  • the impeller comprises seven of the blades, and in the circumferential direction, the angle between adjacent blades is 49.5° to 50.5°, 51.0° to 52.0°, 45.5 to 46.5°, 58.6 to 59.6°. , 47.5 to 48.5 °, 46.8 to 47.3 °, 57.5 ° to 58.5 °.
  • the impeller includes a hub and an outer ring, a radial inner edge of the blade is coupled to the hub, a radial outer edge of the blade is coupled to the outer ring, and a radially outer side of the outer ring is disposed There are grooves.
  • the outer side of the outer ring is provided with a plurality of annular grooves, and the plurality of grooves are arranged along the axial interval of the outer ring.
  • the invention provides a fan.
  • a fan comprising an impeller as described above.
  • the invention provides a fan.
  • a fan includes an impeller as described above and a choke disposed radially outward of the outer ring of the impeller.
  • the blade provided by the invention is provided with at least one concave arc on the trailing edge thereof based on the bionic principle, and a ridge structure is arranged on the blade, and the blade is shaped like a batwing by changing the shape of the blade, thereby improving the airflow of the trailing edge of the blade. Form, which in turn reduces noise.
  • FIG. 1 is a schematic structural view of a blade provided by an embodiment of the present invention.
  • Figure 2 is a schematic illustration of five elementary stages of a blade provided by an embodiment of the present invention.
  • Figure 3 is a perspective view, partly broken away, of the impeller according to an embodiment of the present invention.
  • Figure 4 is a partial enlarged view of a portion A of Figure 4;
  • Figure 5 shows a top view of an impeller provided by an embodiment of the present invention
  • Figure 6 shows a front view of an impeller provided by an embodiment of the present invention
  • Figure 7 is a schematic view showing the structure of the existing outer ring of the impeller and the guide ring;
  • Figure 8 shows a partial cross-sectional view of an impeller provided by an embodiment of the present invention
  • Figure 9 is a partial cross-sectional view showing another impeller provided by an embodiment of the present invention.
  • Figure 10 is a partial cross-sectional view showing still another impeller according to an embodiment of the present invention.
  • Figure 11 is a partial cross-sectional view showing still another impeller according to an embodiment of the present invention.
  • Figure 12 is a graph showing the pressure surface static pressure distribution of a blade provided by an embodiment of the present invention.
  • the present invention provides a blade, as shown in Figures 1 to 4, the blade 1 of the present application is formed as a sheet-like structure comprising a leading edge 11, a trailing edge 12, a radially inner edge 13 and a radially outer edge 14 Providing at least one concave arc 15 on the trailing edge 12 of the blade 1 and at least the concave arc 15 One end point is located between the radially outer edge 13 of the blade 1 and the radially inner edge 14, i.e., at least one end of the concave arc 15 is located radially inward of the radially outer edge 13 of the blade 1 and the diameter of the radially inner edge 14.
  • both ends of the concave arc 15 are located between the radially outer edge 13 of the blade 1 and the radially inner edge 14, based on the principle of bionics, by changing the shape of the blade 1 such that the blade is shaped like a batwing , thereby improving the flow pattern of the trailing edge of the blade, thereby reducing noise.
  • the number of the concave arcs 15 is not limited and can be determined according to factors such as the specific specifications of the blades 1.
  • the specific arc of the concave arc 15 is not limited, and may be a circular arc shape or an arc having a constantly changing curvature.
  • the curvature of the concave arc 15 is from the radially inner edge 13 of the blade 1 to the radially outer edge.
  • the direction of 14 is gradually increased, and a better airflow pattern can be obtained.
  • the blade 1 has a suction surface 17 and a pressure surface 18 on which at least one ridge structure projecting from the pressure surface 18 of the blade 1 toward the suction surface 17 of the blade 1 is provided, that is, at the blade 1
  • the pressure surface 18 forms a recess such that both the pressure surface 18 and the suction surface 17 project along the pressure surface 18 in the direction of the suction surface 17.
  • the ridge structure cooperates with the concave arc 15 on the trailing edge 12 to further improve the flow pattern of the airflow and reduce the broadband noise of the blade 1.
  • the shape of the ridge structure is not limited in particular.
  • the ridge structure has a pointed structure, and the pointed structure is preferably connected to the suction surface 17 of the blade 1 and the pressure surface 18 via a smooth curved surface. It can avoid the occurrence of airflow dead angle and further improve the performance of the fan using it.
  • the arrangement of the ridge structures on the blades is not limited in particular, and preferably one end meets the leading edge 11 of the blade 1 and the other end meets the trailing edge 12 of the blade, in order to be able to form a concave arc 15 on the trailing edge 12 of the blade.
  • one end of the ridge structure meets at the end of the concave arc 15 and the other end meets the leading edge 11 of the blade, so that the ridge structure and the concave arc 15 can form a batwing more closely.
  • the structure allows for a better airflow pattern.
  • the concave arc 15 is disposed in the middle of the radial direction of the blade 1 (the definition of the specific position can be obtained by defining the ridge structure later), and the concave arc 15 has two end points, respectively adjacent to the radially inner edge 13 of the blade.
  • the first end point and the second end point adjacent to the radially outer edge 14 of the blade are provided with two ridge structures on the blade 1, respectively for the first ridge structure 161 disposed near the radially inner edge 13 of the blade and near the blade radial direction.
  • the second ridge structure 162 is disposed on the outer edge 14.
  • the first ridge structure 161 has one end meeting the first end point and the other end and the blade leading edge 11 At the intersection, one end of the second ridge structure 162 meets the second end point, and the other end meets the leading edge 11 of the blade, thus forming a shape very close to the batwing, thereby improving the airflow at the trailing edge 12 of the blade and reducing the generation of the blade. noise.
  • the ridge structure preferably has a circular arc shape in the circumferential direction, and more preferably, in a plane perpendicular to the axial direction, the radially inner edge 13 of the blade 1, the radially outer edge 14, and the first ridge structure 161, the second convex
  • the circle of the ridge structure 162 is concentric.
  • the structural parameters of the various parts of the blade 1 can be optimized.
  • the maximum height of the ridge structure is gradually reduced from the radially inner edge of the blade to the radially outer edge.
  • the maximum height of the ridge structure is the vertical distance of the point of the center line of the blade 1 at the tip end position of the sharp corner structure of the ridge structure from the radially inner edge 13 of the blade 1 to the center line AB of the radial outer edge 14.
  • the maximum height of the first ridge structure 161 is W1
  • the maximum height of the second ridge structure 162 is W2 is smaller than W1.
  • the distance between the radially inner edge 13 of the blade 1 and the radially outer edge 14 is L, and the radial direction described herein is not in a plane perpendicular to the axial direction.
  • the radial direction here is that a radial line is drawn at the center, and the radial line can be combined with the radially inner edge 13 and the radial direction.
  • the edges 14 all have intersections, and the distance between the two intersections is the distance L.
  • the radius of the arc of the first ridge structure 161 in the circumferential direction is R2
  • the radius of the arc of the second ridge structure 162 in the circumferential direction is R3, the radial direction of the blade 1.
  • the five elementary stages are uniformly spaced from the radially inner edge 13 to the radially outer edge 14 of the blade 1 (from the radially inner edge to the radially outer edge in sequence)
  • the cascade consistency is 0.84 to 0.86, 0.77 to 0.79, 0.54 to 0.56, 0.57 to 0.59, 0.51 to 0.53, and the installation angle (from the radially inner edge to the radial direction)
  • the edge is ⁇ 1, ⁇ 2, ⁇ 3, ⁇ 4, ⁇ 5) in order of 30.5 to 32.5, 24.5 to 26.5, 19.5 to 21.5, 15.5 to 17.5, 13.0 to 15.0, and the front bending angle (from the radially inner edge to the radially outer edge)
  • ⁇ 1, ⁇ 2, ⁇ 3, ⁇ 4, and ⁇ 5) are sequentially 0°, 1° to 3°, 7° to 9°, 9° to 11°, and 17° to 19°.
  • the primitive level is the portion where the circumferential surface of the radius R intersects the blade 1 in the axial direction, and the circumferential surface of the different radius R can intersect the blade 1 to form different primitive levels, and the blade is composed of an infinite number of primitives Level composition.
  • the installation angle is the angle between the blade chord and the direction of rotation.
  • the angle of the front bend is the angle between the line between the center of the elementary level and the center of rotation of the blade. By default, the front corner of the first elementary level is 0°. .
  • the present application also provides an impeller that employs a blade as described above.
  • the impeller includes a hub 2, and the radially inner edges 13 of the plurality of blades 1 are fixed to the outer peripheral surface of the hub 2 and distributed in the circumferential direction.
  • the corresponding ridge structures on the plurality of blades 1 are respectively located on the same circle.
  • the first ridge structures 161 of the plurality of blades 1 are all located on the same circle, and the second ridge structures 162 of the plurality of blades 1 are also located on the same circle.
  • the blades of the existing impeller are generally arranged uniformly in the circumferential direction, and the airflow flowing through the blades and the blades are periodically beaten, thereby generating a dipole noise source, that is, the blade passing noise.
  • This type of noise is a narrow-band noise
  • the fundamental frequency noise value is the highest
  • the fundamental frequency increases with the increase of the number of revolutions and the number of blades, and the sound quality is extremely unpleasant and unacceptable.
  • at least one of the angles between adjacent blades 1 is different from the other angles, and the non-equal spacing can control the noise peak to some extent. Especially the peak corresponding to the fundamental frequency.
  • the term "angle” is defined as the angle between the radially outer end of the leading edge of the blade and the center line.
  • the impeller includes seven blades 1, and in the circumferential direction, the angle between adjacent blades 1 is ⁇ 1, ⁇ 2, ⁇ 3, ⁇ 4, ⁇ 5, ⁇ 6, ⁇ 7, respectively.
  • ⁇ 1 ranges from 49.5° to 50.5°
  • ⁇ 2 ranges from 51.0° to 52.0°
  • ⁇ 3 ranges from 45.5 to 46.5°
  • ⁇ 4 ranges from 58.6 to 59.6°
  • ⁇ 5 ranges from 47.5 to 48.5°
  • ⁇ 6 ranges It is 46.8 to 47.3°
  • the range of ⁇ 7 is 57.5° to 58.5°.
  • the impeller further comprises an outer ring 3, the radially inner edge 13 of which is connected to the hub 2, and the radially outer edge 14 is connected to the outer ring 3.
  • the impeller is mounted on the fan, the impeller is disposed in the choke, that is, the choke is placed on the outer circumference of the impeller such that the choke is located radially outward of the outer ring 3.
  • a safety gap is provided between the outer ring 3' and the draft ring 4'.
  • Airflow inevitably flows through the gap, causing leakage, resulting in reduced fan efficiency.
  • a groove 31 is provided on the radially outer side of the outer ring 3, so that the cross-sectional area of the outer ring 3 is repeatedly changed, thereby increasing the outer ring 3 and the draft ring. The resistance of the flow path formed between the two, so that the safety gap can be ensured while reducing the leakage, thereby improving the efficiency of the fan.
  • the size of the groove 31 should not be too large, and should not be too small, too much influence the structural strength of the outer ring 3, and if it is too small, the effect of increasing the resistance is not obtained.
  • the depth of the groove 31 is M1 ⁇ 0.5 M2, and M2 is the thickness of the outer ring.
  • the width of the groove 31 (i.e., the dimension in the axial direction) M3 ranges from M1 ⁇ M3 ⁇ 2M1.
  • the specific shape of the groove 31 is not limited, and is preferably annular, and a plurality of annular grooves 31 are spaced apart along the axial direction of the outer ring 3, thereby achieving a better effect of increasing the resistance.
  • the cross-sectional shape of the groove 31 is not limited, and may be an arc as shown in FIG. 8, or may be a polygon, for example, a rectangle, a semi-pentagon, a semi-hexagon, etc. as shown in FIGS. 9 to 11, the cross section.
  • the polygonal groove can further increase the resistance to the airflow and reduce the leakage of the fan.
  • the present application further provides a fan, which adopts the above-mentioned impeller, can effectively reduce the noise of the fan and is more reliable in operation, less leakage, and high efficiency.
  • the mounting angles are 0.85, 0.78, 0.55, 0.58, and 0.52, and the mounting angles are 31.5°, 25.5°, 20.5°, 16.5°, and 14.0°, respectively, and the front bending angles are 0°, 2°, 8°, 10°, and 18°, respectively.
  • the angles of ⁇ 1, ⁇ 2, ⁇ 3, ⁇ 4, ⁇ 5, ⁇ 6, and ⁇ 7 are 50°, 51.5°, 46°, 59.1°, 48°, 47.3°, and 58°, respectively.
  • M1 0.5 M2
  • M2 is the thickness of the outer ring
  • M3 M1
  • the cross-sectional shape of the groove is an arc as shown in FIG.
  • the fan of the present application has high efficiency and low noise, and the efficiency is 2.18% higher than that of the existing fan, and the noise is reduced by 2.5 dB, which has better performance than the existing fan.
  • the fan provided by the present application can be widely applied to various devices that need to supply air, for example, for air conditioners, especially bus air conditioners.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

一种叶片、叶轮及风机。该叶片(1)的尾缘(12)设置有至少一段内凹弧(15)，至少一段内凹弧(15)的至少一个端点位于所述叶片(1)的径向外缘(13)与径向内缘(14)之间，所述叶片(1)上设置有至少一条由所述叶片(1)的压力面(18)向所述叶片(1)的吸力面(17)方向凸出的凸脊结构。该叶片基于仿生原理在其尾缘设置至少一段内凹弧，且在叶片上设置凸脊结构，通过改变叶片的形状，改善叶片尾缘气流流动形态，进而降低噪音。

Description

叶片、叶轮及风机 技术领域
本发明涉及风机领域，更具体地涉及一种叶片、叶轮及风机。
背景技术
在风机的转速较高时，尤其转速在3200Rpm左右时，气流流经叶片表面时会出现边界层分离严重、叶片尾缘处气流紊动强烈的状况，进而导致叶片宽频噪音较高，影响风机的性能且使用舒适度低。
发明内容
有鉴于此，本发明的目的之一是提供一种能够提高风机性能、降低叶片宽频噪音的叶片、叶轮及风机。
为达上述目的，第一方面，提供一种叶片。
一种叶片，所述叶片的尾缘设置有至少一段内凹弧，所述至少一段内凹弧的至少一个端点位于所述叶片的径向外缘与径向内缘之间，所述叶片上设置有至少一条由所述叶片的压力面向所述叶片的吸力面方向凸出的凸脊结构。
优选地，所述凸脊结构的一端交汇于所述内凹弧的端点处，另一端交汇于所述叶片的前缘。
优选地，每一段所述内凹弧的两个端点均对应设置一条所述凸脊结构。
优选地，所述叶片上由所述叶片的径向内缘向径向外缘的方向间隔设置有多条凸脊结构，所述凸脊结构的最大高度由所述叶片的径向内缘向径向外缘的方向逐渐减小。
优选地，所述叶片的尾缘设置有一段内凹弧，所述至少一条由所述叶片的压力面向所述叶片的吸力面方向凸出的凸脊结构包括靠近所述叶片的径向内缘设置的第一凸脊结构和靠近所述叶片的径向外缘设置的第 二凸脊结构，所述第一凸脊结构的一端交汇于所述内凹弧上靠近所述叶片的径向内缘的端点处，所述第二凸脊结构交汇于所述内凹弧上靠近所述叶片的径向外缘的端点处。
优选地，所述第一凸脊结构的最大高度为W1，所述第二凸脊结构的最大高度为W2，在径向上，所述叶片的径向内缘与径向外缘之间的距离为L；
其中，W1＝k1*L，系数k1的范围为0.025至0.035；和/或，
W2＝k2*L，系数k2的范围为0.021至0.031。
优选地，所述凸脊结构呈圆弧形。
优选地，所述叶片的尾缘设置有一段内凹弧，所述至少一条由所述叶片的压力面向所述叶片的吸力面方向凸出的凸脊结构包括靠近所述叶片的径向内缘设置的第一凸脊结构和靠近所述叶片的径向外缘设置的第二凸脊结构，所述第一凸脊结构的一端交汇于所述内凹弧上靠近所述叶片的径向内缘的端点处，所述第二凸脊结构交汇于所述内凹弧上靠近所述叶片的径向外缘的端点处，所述第一凸脊结构在周向上的圆弧半径为R2，所述第二凸脊结构在周向上的圆弧半径为R3，所述叶片的径向内缘的半径为R1；
其中，R2＝k3*R1，系数k3的范围为1.3至1.4；和/或，
R3＝k4*R1，系数k4的范围为1.95至2.05。
优选地，所述凸脊结构的圆心与所述叶片的径向内缘的圆心重合。
优选地，所述叶片的尾缘设置有一段内凹弧，在所述叶片自其径向内缘向径向外缘依次均布的五个基元级中，
叶栅稠度依次为0.84至0.86,0.77至0.79,0.54至0.56,0.57至0.59,0.51至0.53；和/或，
安装角度依次为30.5至32.5,24.5至26.5,19.5至21.5,15.5至17.5,13.0至15.0；和/或，
前弯角度依次为0°，1°至3°，7°至9°，9°至11°，17°至19°。
优选地，所述凸脊结构具有尖角结构，所述尖角结构与所述叶片的吸力面和压力面均经平滑曲面过渡连接。
第二方面，本发明提供一种叶轮。
一种叶轮，包括如上所述的叶片。
优选地，所述叶轮包括多个沿周向排布的所述叶片，相邻叶片之间具有夹角，在所述夹角中，至少有一个夹角的度数与其他夹角的度数不同。
优选地，所述叶轮包括7个所述叶片，在周向上，相邻所述叶片之间的夹角依次为49.5°至50.5°，51.0°至52.0°，45.5至46.5°，58.6至59.6°，47.5至48.5°，46.8至47.3°，57.5°至58.5°。
优选地，所述叶轮包括轮毂和外圈，所述叶片的径向内缘与所述轮毂连接，所述叶片的径向外缘与所述外圈连接，所述外圈的径向外侧设置有凹槽。
优选地，所述外圈的径向外侧设置多条呈环形的所述凹槽，多条所述凹槽沿所述外圈的轴向间隔分布设置。
第三方面，本发明提供一种风机。
一种风机，包括如上所述的叶轮。
第四方面，本发明提供一种风机。
一种风机，包括如上所述的叶轮以及设置于所述叶轮的外圈径向外侧的导流圈。
本发明提供的叶片基于仿生原理在其尾缘设置至少一段内凹弧，且在叶片上设置凸脊结构，通过改变叶片的形状使得叶片呈类似于蝙蝠翼的形状，从而改善叶片尾缘气流流动形态，进而降低噪音。
附图说明
通过以下参照附图对本发明实施例的描述，本发明的上述以及其它目的、特征和优点将更为清楚，在附图中：
图1示出本发明具体实施方式提供的叶片的结构示意图；
图2示出本发明具体实施方式提供的叶片的五个基元级的示意图；
图3示出本发明具体实施方式提供的叶轮局部剖视开的立体图；
图4示出图4中A部分的局部放大图；
图5示出本发明具体实施方式提供的叶轮的俯视图；
图6示出本发明具体实施方式提供的叶轮的主视图；
图7示出现有叶轮外圈与导流圈配合处的结构示意图；
图8示出本发明具体实施方式提供的叶轮的局部剖视图；
图9示出本发明具体实施方式提供的另一种叶轮的局部剖视图；
图10示出本发明具体实施方式提供的再一种叶轮的局部剖视图；
图11示出本发明具体实施方式提供的还一种叶轮的局部剖视图；
图12示出本发明具体实施方式提供的叶片的压力面静压分布图。
图中，1、叶片；11、前缘；12、尾缘；13、径向内缘；14、径向外缘；15、内凹弧；161、第一凸脊结构；162、第二凸脊结构；17、吸力面；18、压力面；2、轮毂；3、外圈；31、凹槽；3’外圈；4’、导流圈。
具体实施方式
以下基于实施例对本发明进行描述，但是本发明并不仅仅限于这些实施例。在下文对本发明的细节描述中，详尽描述了一些特定的细节部分。对本领域技术人员来说没有这些细节部分的描述也可以完全理解本发明。为了避免混淆本发明的实质，公知的方法、过程、流程、元件并没有详细叙述。
此外，本领域普通技术人员应当理解，在此提供的附图都是为了说明的目的，并且附图不一定是按比例绘制的。
除非上下文明确要求，否则整个说明书和权利要求书中的“包括”、“包含”等类似词语应当解释为包含的含义而不是排他或穷举的含义；也就是说，是“包括但不限于”的含义。
在本发明的描述中，需要理解的是，术语“第一”、“第二”等仅用于描述目的，而不能理解为指示或暗示相对重要性。此外，在本发明的描述中，除非另有说明，“多个”的含义是两个或两个以上。
本发明提供了一种叶片，如图1至图4所示，本申请中的叶片1形成为片状结构，其包括前缘11、尾缘12、径向内缘13与径向外缘14，在叶片1的尾缘12上设置有至少一段内凹弧15，且该内凹弧15的至少 一个端点位于叶片1的径向外缘13与径向内缘14之间，即内凹弧15的至少一个端点位于叶片1的径向外缘13的径向内侧以及径向内缘14的径向外侧，优选内凹弧15的两个端点均位于叶片1的径向外缘13与径向内缘14之间，基于仿生原理，通过改变叶片1的形状使得叶片呈类似于蝙蝠翼的形状，从而改善叶片尾缘气流流动形态，进而降低噪音。
内凹弧15的数量不限，可根据叶片1的具体规格等因素进行确定。内凹弧15的具体弧度不限，也可以为圆弧形，也可以为曲率不断变化的弧形，优选地，内凹弧15的曲率由叶片1的径向内缘13向径向外缘14的方向逐渐增大，能够获得更优的气流流动形态。
进一步优选地，叶片1具有吸力面17和压力面18，在叶片1上设置有至少一条由叶片1的压力面18向叶片1的吸力面17方向凸出的凸脊结构，即在叶片1的压力面18形成凹部，使得压力面18和吸力面17均沿压力面18向吸力面17的方向凸出。如此，凸脊结构与尾缘12上的内凹弧15相配合来进一步改善气流的流动形态，降低叶片1的宽频噪音。凸脊结构的形状具体不限，在一个优选地实施例中，凸脊结构呈尖角结构，并且，尖角结构优选与叶片1的吸力面17以及压力面18经平滑曲面过渡连接，如此，能够避免产生气流死角，进一步提高采用其的风机性能。
凸脊结构在叶片上的排布方式具体不限，优选一端交汇于叶片1的前缘11，另一端交汇于叶片的尾缘12，为了能够与叶片尾缘12上的内凹弧15形成更好的配合，进一步优选地，凸脊结构的一端交汇于内凹弧15的端点处，另一端交汇于叶片的前缘11，如此，凸脊结构与内凹弧15能够形成更加近似于蝙蝠翼的结构，从而获得更优的气流流动形态。
下面以在尾缘12设置一段内凹弧15为例具体说明内凹弧15与凸脊结构的具体配合结构。内凹弧15设置在叶片1径向的中部(对具体位置的限定可通过后面对凸脊结构的限定获得)，内凹弧15具有两个端点，分别为靠近叶片径向内缘13的第一端点以及靠近叶片径向外缘14的第二端点，叶片1上设置有两条凸脊结构，分别为靠近叶片径向内缘13设置的第一凸脊结构161以及靠近叶片径向外缘14设置的第二凸脊结构162，第一凸脊结构161的一端与第一端点交汇，另一端与叶片前缘11 交汇，第二凸脊结构162的一端与第二端点交汇，另一端与叶片前缘11交汇，如此，形成非常接近于蝙蝠翼的形状，从而改善叶片尾缘12处的气流，降低叶片产生的噪音。
凸脊结构优选在周向上呈圆弧形，进一步优选地，在与轴向垂直的平面内，叶片1的径向内缘13、径向外缘14以及第一凸脊结构161、第二凸脊结构162所在圆为同心圆。
为进一步优化气流的流动形态，可对叶片1的各部分结构参数进行优化，在优选的实施例中，凸脊结构的最大高度由叶片的径向内缘向径向外缘的方向逐渐减小，凸脊结构的最大高度为叶片1的中线在凸脊结构的尖角结构顶端位置上的点距离叶片1的径向内缘13至径向外缘14的重心连线AB的垂直距离。在如图4中所示的实施例中，第一凸脊结构161的最大高度为W1，第二凸脊结构162的最大高度为W2，W2小于W1。
进一步优选地，如图4所示，在径向上，叶片1的径向内缘13与径向外缘14之间的距离为L，此处所述的径向不是在与轴向垂直平面内的投影方向上，由于叶片1安装后相对于轴线方向有一定的夹角，因此，此处的径向是，在中心引出一条径线，该径线能够与径向内缘13和径向外缘14均具有交点，这两个交点之间的距离即为距离L。W1与L优选满足关系：W1＝k1*L，系数k1的范围为0.025至0.035。W2与L优选满足关系：W2＝k2*L，系数k2的范围为0.021至0.031。
在优选的实施例中，如图5所示，第一凸脊结构161在周向上的圆弧半径为R2，第二凸脊结构162在周向上的圆弧半径为R3，叶片1的径向内缘13的半径为R1，R1与R2优选满足关系：R2＝k3*R1，系数k3的范围为1.3至1.4。R1与R3优选满足关系：R3＝k4*R1，系数k4的范围为1.95至2.05。
在优选的实施例中，如图2所示，在叶片1自其径向内缘13向径向外缘14依次均布的五个基元级(自径向内缘向径向外缘依次为S1、S2、S3、S4、S5)中，叶栅稠度依次为0.84至0.86,0.77至0.79,0.54至0.56,0.57至0.59,0.51至0.53，安装角度(自径向内缘向径向外缘依次为β1、β2、β3、β4、β5)依次为30.5至32.5,24.5至26.5,19.5至21.5,15.5至17.5,13.0至15.0，前弯角度(自径向内缘向径向外缘 依次为σ1、σ2、σ3、σ4、σ5)依次为0°，1°至3°，7°至9°，9°至11°，17°至19°。其中，基元级为半径R的圆周面沿轴向与叶片1相交时两者相交的部分，不同半径R的圆周面能够与叶片1相交成不同的基元级，叶片由无限多个基元级构成。安装角度为叶片翼弦与旋转方向的夹角，前弯角度为不同的基元级中心与叶片旋转中心之间的连线的夹角，默认第一个基元级的前弯角为0°。
进一步地，本申请还提供了一种叶轮，其采用如上所述的叶片。在一个具体的实施例中，如图3至图6所示，叶轮包括轮毂2，多个叶片1的径向内缘13固定于轮毂2的外周面上并沿周向分布。优选的，在与轮毂2的轴线垂直的平面内，多个叶片1上相对应的凸脊结构分别位于同一个圆上。例如，如图5中所示，多个叶片1的第一凸脊结构161均位于同一个圆上，多个叶片1的第二凸脊结构162也位于同一个圆上。
现有叶轮的叶片一般在周向上为均匀布置，流经叶片的气流与叶片产生周期拍打的现象，从而产生偶极子噪声源，也即为叶片通过噪音。该类型噪音属于窄频噪音，基频噪音值最高，而且基频随着转速以及叶片数的增加而增加，音质听起来极不悦耳，难以令人接受。针对此问题，本申请中，相邻叶片1之间的夹角中，至少有一个夹角的度数与其他夹角的度数不同，这种非等间距的设置方式能够在一定程度上控制噪音峰值，尤其是基频所对应的峰值。
本申请中对于“夹角”的定义为，叶片前缘的径向外端与中心连线之间的夹角。在一个具体的实施例中，如图5所示，叶轮包括7个叶片1，在周向上，相邻叶片1之间的夹角依次为θ1、θ2、θ3、θ4、θ5、θ6、θ7，θ1的范围为49.5°至50.5°，θ2的范围为51.0°至52.0°，θ3的范围为45.5至46.5°，θ4的范围为58.6至59.6°，θ5的范围为47.5至48.5°，θ6的范围为46.8至47.3°，θ7的范围为57.5°至58.5°。
在进一步的实施例中，叶轮还包括外圈3，叶片1的径向内缘13与轮毂2连接，径向外缘14与外圈3连接。当叶轮安装在风机上时，叶轮设置在导流圈内，即导流圈罩于叶轮的外周上，使得导流圈位于外圈3的径向外侧。
现有技术中，如图7所示，为了防止外圈3’与导流圈4’出现动静干涉，在外圈3’与导流圈4’之间会设置安全间隙，在风机运转过程中，气流不可避免的会流经该间隙，从而发生泄漏，导致风机效率降低。为改善这一现象，本申请中，如图8所示，在外圈3的径向外侧设置有凹槽31，使得外圈3的截面面积会发生反复变化，从而增加外圈3与导流圈之间形成的流道的阻力，如此，能够在保证安全间隙的同时，减少泄漏，进而提高风机效率。
凹槽31的尺寸不宜过大，也不宜过小，过大会影响外圈3的结构强度，过小则起不到增加阻力的效果。在一个优选的实施例中，凹槽31的深度M1≤0.5M2，M2为外圈的厚度。凹槽31的宽度(即在轴向上的尺寸)M3的取值范围为M1<M3<2M1。
凹槽31的具体形状不限，优选呈环形，多条环形的凹槽31沿外圈3的轴向间隔分布设置，从而达到更好的增加阻力的效果。凹槽31的截面形状也不限，可以为如图8所示的弧形，也可以为多边形，例如如图9至11所示的矩形、半五边形、半六边形等等，截面呈多边形的凹槽能够进一步的增加对气流的阻力，降低风机的泄露。
进一步地，本申请还提供了一种风机，采用上述的叶轮，能够有效降低风机的噪音且运行更加可靠，泄露少，效率高。
在一个具体的实施例中，该风机的叶片具体参数为，R2＝1.33R1，R3＝1.99R1，W1＝0.299L，W2＝0.026L，S1、S2、S3、S4、S5的叶栅稠度分别为0.85、0.78、0.55、0.58、0.52，安装角度分别为31.5°、25.5°、20.5°、16.5°、14.0°，前弯角度分别为0°、2°、8°、10°、18°。θ1、θ2、θ3、θ4、θ5、θ6、θ7的角度依次为50°、51.5°、46°、59.1°、48°、47.3°、58°。叶轮外圈的凹槽深度M1＝0.5M2，M2为外圈厚度，凹槽宽度M3＝M1，凹槽的截面形状为如图8中所示的弧形。经模拟实验，该风机的叶片的压力面静压分布如图12所示，由图可知，通过一系列的尺寸优化，进一步地改善气流的流动形态，降低叶片的宽频噪音。经具体的实验测试，与现有风机的对比结果如下表所示：
Figure PCTCN2017103960-appb-000001
由上表可知，本申请风机的效率高且噪音低，效率相较于现有风机提高了2.18％，噪音降低了2.5dB，较现有风机具有更好的性能。
本申请提供的风机可广泛应用于各种需要进行送风的设备中，例如适用于空调，尤其是大巴空调中。
本领域的技术人员容易理解的是，在不冲突的前提下，上述各优选方案可以自由地组合、叠加。
应当理解，上述的实施方式仅是示例性的，而非限制性的，在不偏离本发明的基本原理的情况下，本领域的技术人员可以针对上述细节做出的各种明显的或等同的修改或替换，都将包含于本发明的权利要求范围内。

Claims (18)

  1. 一种叶片，其特征在于，所述叶片的尾缘设置有至少一段内凹弧，所述至少一段内凹弧的至少一个端点位于所述叶片的径向外缘与径向内缘之间，所述叶片上设置有至少一条由所述叶片的压力面向所述叶片的吸力面方向凸出的凸脊结构。
  2. 根据权利要求1所述的叶片，其特征在于，所述凸脊结构的一端交汇于所述内凹弧的端点处，另一端交汇于所述叶片的前缘。
  3. 根据权利要求2所述的叶片，其特征在于，每一段所述内凹弧的两个端点均对应设置一条所述凸脊结构。
  4. 根据权利要求1所述的叶片，其特征在于，所述叶片上由所述叶片的径向内缘向径向外缘的方向间隔设置有多条凸脊结构，所述凸脊结构的最大高度由所述叶片的径向内缘向径向外缘的方向逐渐减小。
  5. 根据权利要求1所述的叶片，其特征在于，所述叶片的尾缘设置有一段内凹弧，所述至少一条由所述叶片的压力面向所述叶片的吸力面方向凸出的凸脊结构包括靠近所述叶片的径向内缘设置的第一凸脊结构和靠近所述叶片的径向外缘设置的第二凸脊结构，所述第一凸脊结构的一端交汇于所述内凹弧上靠近所述叶片的径向内缘的端点处，所述第二凸脊结构交汇于所述内凹弧上靠近所述叶片的径向外缘的端点处。
  6. 根据权利要求5所述的叶片，其特征在于，所述第一凸脊结构的最大高度为W1，所述第二凸脊结构的最大高度为W2，在径向上，所述叶片的径向内缘与径向外缘之间的距离为L；
    其中，W1＝k1*L，系数k1的范围为0.025至0.035；和/或，
    W2＝k2*L，系数k2的范围为0.021至0.031。
  7. 根据权利要求1所述的叶片，所述凸脊结构在周向上呈圆弧形。
  8. 根据权利要求7所述的叶片，其特征在于，所述叶片的尾缘设置有一段内凹弧，所述至少一条由所述叶片的压力面向所述叶片的吸力面方向凸出的凸脊结构包括靠近所述叶片的径向内缘设置的第一凸脊结构和靠近所述叶片的径向外缘设置的第二凸脊结构，所述第一凸脊结构的一端交汇于所述内凹弧上靠近所述叶片的径向内缘的端点处，所述第二凸脊结构交汇于所述内凹弧上靠近所述叶片的径向外缘的端点处，所述第一凸脊结构在周向上的圆弧半径为R2，所述第二凸脊结构在周向上的圆弧半径为R3，所述叶片的径向内缘的半径为R1；
    其中，R2＝k3*R1，系数k3的范围为1.3至1.4；和/或，
    R3＝k4*R1，系数k4的范围为1.95至2.05。
  9. 根据权利要求7所述的叶片，其特征在于，所述凸脊结构的圆心与所述叶片的径向内缘的圆心重合。
  10. 根据权利要求5所述的叶片，其特征在于，在所述叶片自其径向内缘向径向外缘依次均布的五个基元级中，
    叶栅稠度依次为0.84至0.86,0.77至0.79,0.54至0.56,0.57至0.59,0.51至0.53；和/或，
    安装角度依次为30.5至32.5,24.5至26.5,19.5至21.5,15.5至17.5,13.0至15.0；和/或，
    前弯角度依次为0°，1°至3°，7°至9°，9°至11°，17°至19°。
  11. 根据权利要求1所述的叶片，其特征在于，所述凸脊结构具有尖角结构，所述尖角结构与所述叶片的吸力面和压力面均经平滑曲面过渡连接。
  12. 一种叶轮，其特征在于，包括如权利要求1至11任一项所述 的叶片。
  13. 根据权利要求12所述的叶轮，其特征在于，所述叶轮包括多个沿周向排布的所述叶片，相邻叶片之间具有夹角，在所述夹角中，至少有一个夹角的度数与其他夹角的度数不同。
  14. 根据权利要求13所述的叶轮，其特征在于，所述叶轮包括7个所述叶片，在周向上，相邻所述叶片之间的夹角依次为49.5°至50.5°，51.0°至52.0°，45.5至46.5°，58.6至59.6°，47.5至48.5°，46.8至47.3°，57.5°至58.5°。
  15. 根据权利要求12至14任一项所述的叶轮，其特征在于，所述叶轮包括轮毂和外圈，所述叶片的径向内缘与所述轮毂连接，所述叶片的径向外缘与所述外圈连接，所述外圈的径向外侧设置有凹槽。
  16. 根据权利要求15所述的叶轮，其特征在于，所述外圈的径向外侧设置多条呈环形的所述凹槽，多条所述凹槽沿所述外圈的轴向间隔分布设置。
  17. 一种风机，其特征在于，包括如权利要求12至16任一项所述的叶轮。
  18. 一种风机，其特征在于，包括如权利要求15或16所述的叶轮以及设置于所述叶轮的外圈径向外侧的导流圈。
PCT/CN2017/103960 2017-01-06 2017-09-28 叶片、叶轮及风机 Ceased WO2018126745A1 (zh)

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