WO2019006971A1 - Roue, ventilateur et moteur - Google Patents

Roue, ventilateur et moteur Download PDF

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Publication number
WO2019006971A1
WO2019006971A1 PCT/CN2017/113990 CN2017113990W WO2019006971A1 WO 2019006971 A1 WO2019006971 A1 WO 2019006971A1 CN 2017113990 W CN2017113990 W CN 2017113990W WO 2019006971 A1 WO2019006971 A1 WO 2019006971A1
Authority
WO
WIPO (PCT)
Prior art keywords
blade
impeller
trailing edge
impeller according
hub
Prior art date
Application number
PCT/CN2017/113990
Other languages
English (en)
Chinese (zh)
Inventor
蒋婷婷
冯国平
Original Assignee
广东威灵电机制造有限公司
美的威灵电机技术（上海）有限公司
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
Priority claimed from CN201720799224.2U external-priority patent/CN206874553U/zh
Priority claimed from CN201710531117.6A external-priority patent/CN107143523A/zh
Application filed by 广东威灵电机制造有限公司, 美的威灵电机技术（上海）有限公司 filed Critical 广东威灵电机制造有限公司
Priority to KR1020197031208A priority Critical patent/KR20190125501A/ko
Priority to JP2019560378A priority patent/JP2020518761A/ja
Publication of WO2019006971A1 publication Critical patent/WO2019006971A1/fr

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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
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—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
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/08—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation
    • 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
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal 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
    • F05D2210/00—Working fluids
    • F05D2210/10—Kind or type
    • F05D2210/12—Kind or type gaseous, i.e. compressible
    • 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

Definitions

  • the invention belongs to the field of impellers, and more particularly to an impeller and a fan and an electric machine therewith.
  • the impeller In the vacuum cleaner, the impeller is driven to rotate at a high speed by a motor to form a negative pressure environment in the sealed casing, so that dust and the like are sucked into the dust collecting device, thereby achieving a cleaning effect.
  • the impeller is a key component of the vacuum cleaner, and its performance directly determines the overall working efficiency of the fan system.
  • the vacuum cleaners in the prior art generally have the disadvantages of large volume and low performance of the fan, and it is necessary to continuously optimize the design of the impeller structure to further improve the working performance of the vacuum cleaner.
  • the present invention provides an impeller capable of optimizing work performance.
  • the present invention provides an impeller including a substantially conical hub and a plurality of blades circumferentially spaced apart on an outer peripheral surface of the hub, the blades including a leading edge at an inlet end The face and the trailing edge face at the outlet end, the blade being a flat twisted blade, the blade trailing edge section of the blade being tilted with respect to the circumferential direction.
  • the trailing edge section of the blade is inclined toward the upstream side with respect to the direction of rotation of the impeller.
  • the inclined angle ⁇ of the trailing edge section of the blade toward the upstream side is not more than 40°.
  • the upstream side surface of the trailing edge section of the blade is formed as a concave surface and the downstream side surface is formed as a convex surface, the length of the convex surface occupies 50% to 90% of the total length of the blade.
  • the leading edge face is an inclined plane with respect to a central axis of the hub, the angle of the inclined plane with respect to the central axis being ⁇ , and satisfying: 30° ⁇ ⁇ ⁇ 90°.
  • the blade includes a blade root connected to an outer peripheral surface of the hub and extending from the leading edge face to the trailing edge face and extending from a tip end of the leading edge face to the trailing edge face
  • the top surface of the tip of the blade gradually decreases in height from the leading edge toward the trailing edge surface with respect to the height of the blade root.
  • the blade root edge line of the blade root is a smooth curve extending from the bottom end of the leading edge face to the bottom end of the trailing edge face.
  • the height b1 of the leading edge face and the height b2 of the trailing edge face respectively satisfy: 5 mm ⁇ b1 ⁇ 9 mm, and 2 mm ⁇ b2 ⁇ 5 mm.
  • the blade has an inlet mounting angle of ⁇ 1, an outlet mounting angle of ⁇ 2, and satisfies: 30° ⁇ 1 ⁇ 80°, 40° ⁇ ⁇ 2 ⁇ 80°.
  • the fan-shaped distribution area of a single of the blades has an angular angle of ⁇ and 50° ⁇ ⁇ ⁇ 100°.
  • 5 to 12 of the blades are distributed on the outer circumferential surface of the hub at equal intervals in the circumferential direction.
  • the present invention accordingly provides a fan and an electric motor each including the above-described impeller.
  • the shape of the blade is optimized in the impeller of the present invention, especially in the trailing edge section, the rear edge section of the flat twisted blade is inclined at an angle with respect to the rotation direction of the impeller toward the upstream side, so that The upstream side of the trailing edge section of the blade is formed into a concave surface, which can effectively reduce the fluid loss at the outlet end of the blade, expand the effective working range of the impeller, and greatly improve the working performance of the impeller.
  • Figure 1 is a perspective view of an impeller in accordance with a preferred embodiment of the present invention.
  • Figure 2 is a front elevational view of the impeller of Figure 1;
  • Figure 3 is a plan view of the impeller of Figure 1.
  • orientation words such as “up, down, top, and bottom” are generally used for the directions shown in the drawings or for vertical, vertical or gravity directions, unless otherwise stated.
  • the components are described in terms of their positional relationship.
  • the present invention provides an impeller 100 including a substantially conical hub 11 and a plurality of blades 12 circumferentially spaced apart on the outer peripheral surface of the hub 11, each blade 12 being located The leading edge face 121 of the inlet end and the trailing edge face 122 at the outlet end, the blade 12 being a flat plate twisting blade, the blade trailing edge section of the blade 12 being tilted with respect to the circumferential direction.
  • the trailing edge section of the blade is tilted toward the upstream side 21 with respect to the direction of rotation w of the impeller 100. It should be noted that the trailing edge portion of the blade is not limited to being twisted toward the upstream side 21, and the same impeller 100 may be rotated in the opposite direction to the illustrated rotational direction w, but the efficiency is relatively poor.
  • the impeller 100 of the present invention can effectively reduce the fluid loss at the outlet end of the blade 12, and enlarge the working area of the impeller 100 under a small flow rate, that is, increase the effective working range and greatly improve The working performance of the impeller 100.
  • the inclination angle ⁇ of the trailing edge section of the blade 12 toward the upstream side 21 is not more than 40°, that is, satisfy: 0 ⁇ ⁇ ⁇ 40°, see FIG. 2 .
  • ⁇ may be 15°, 25°, 40°, etc., and may be specifically set according to actual conditions.
  • each of the vanes 12 extends from the leading edge surface 121 to the trailing edge surface 122 on the outer peripheral surface of the hub 11, and a section of the vane adjacent to the trailing edge surface 122 is formed into a concave surface 126 on the upstream side after the twist is generated.
  • the side on the downstream side is formed as a corresponding convex surface 125, and the length of the convex surface 125 is limited to 50% to 90% of the total length of the blade 12.
  • This streamlined design of the blade 12 facilitates reducing the loss of fluid within the blade passage and improving the flow characteristics of the fluid, thereby improving the performance of the impeller 100.
  • the leading edge surface 121 of the blade 12 is an inclined plane with respect to a central axis of the substantially conical shape of the hub 11, the angle of the inclined plane with respect to the central axis is ⁇ and satisfies: 30° ⁇ ⁇ ⁇ 90°, that is, when the fluid flows in from the leading edge surface 121 of each blade 12, it flows in an oblique direction, effectively controlling the wind pressure at the inlet end of the blade 12, and reducing the loss of the fluid at the inlet end.
  • the blade 12 includes a blade root portion 124 coupled to an outer peripheral surface of the hub 11 and extending from the leading edge surface 121 to the trailing edge surface 122 and extending from a tip end of the leading edge surface 121 to the trailing edge surface
  • the tip top surface 123 of the tip end 122 of the 122 gradually decreases in height from the leading edge surface 121 toward the trailing edge surface 122 with respect to the blade root portion 124.
  • the height b1 from the front edge surface 121 of the blade 12 to the height b2 of the trailing edge surface 122 is gradually decreased.
  • it preferably satisfies: 5 mm ⁇ b1 ⁇ 9 mm, and 2 mm ⁇ b2 ⁇ 5 mm, respectively.
  • the height value b1 of the tip surface 123 of the leading edge surface 121 of each blade 12 with respect to the blade root portion 124 is the largest, and is limited to 5 mm ⁇ b1 ⁇ 9 mm, and the tip of the trailing edge surface 121 of each blade 12
  • the height value b2 of the face 123 with respect to the blade root 124 is the smallest and is limited to 2 mm ⁇ b2 ⁇ 5 mm, and the height between the maximum height b1 and the minimum height b2 of the blade 12 is gradually decreasing.
  • the root edge line of the blade root 124 is preferably a smooth curve extending from the bottom end of the leading edge face 121 to the bottom end of the trailing edge face 122.
  • the inlet angle of the inlet of the blade 12 is ⁇ 1, the angle of installation of the outlet is ⁇ 2, and it satisfies: 30° ⁇ ⁇ 1 ⁇ 80°, 40° ⁇ ⁇ 2 ⁇ 80°.
  • the blade root edge line of the blade root portion 124 of the blade 12 is the intersection line of the side surface of the blade 12 and the outer circumferential surface of the hub 11 , that is, the intersection curve between the face and the face, whereby the blade 12
  • the inlet mounting angle is the angle between the first tangent and the second tangent at the leading edge point of the blade root edge line.
  • the first tangent is a tangent to a leading edge point of the blade root edge line with respect to the blade root edge line
  • the second tangent is the distance from the foremost edge point to the central axis of the hub 11 with the leading edge point being The tangent of the circle of the radius.
  • the exit mounting angle is the tangent angle at the last edge of the blade root edge line, ie the tangent to the last edge point relative to the blade root edge line and the last edge point relative to the center of the last edge point and hub 11
  • the axis is at an angle ⁇ 2 between the tangent to the circle of the radius.
  • the sector angle of the sector-shaped distribution region of a single of said blades is ⁇ , and 50° ⁇ ⁇ ⁇ 100°. That is, the radial divergence line between the most upstream point of each blade 12 and the central axis of the hub and the radial divergence line of the most downstream point and the central axis of the hub, the line formed by the two radial divergence lines
  • the included angle is ⁇ , that is, the circumferential angle of each blade 12 on the outer peripheral surface of the hub 11.
  • All of the impellers 100 mentioned in the present embodiment have 5 to 12 of the blades 12 equally spaced in the circumferential direction on the outer circumferential surface of the hub 11.
  • the present invention also provides a fan including the above-described impeller 100.
  • the impeller 100 By using the impeller 100, the overall performance of the fan can be improved.
  • the present invention also provides an electric machine comprising the above-described impeller 100, by which the overall performance of the electric machine can also be improved.
  • the vacuum cleaner is tested below.
  • the fan in the vacuum cleaner uses different impellers.
  • Table 1 below shows performance test data for the examples of the impellers of the present invention and the comparative examples of the impellers of the prior art, respectively.
  • the US-based S3-L041C vacuum cleaner is commonly used.
  • the vacuum cleaner in the embodiment of the present invention adopts the impeller structure shown in FIG. 1 to FIG. 3 , specifically, the blade is a flat twisted blade and the trailing edge section of the blade is tilted toward the upstream side 21 with respect to the rotational direction w, Embodiment 1
  • the tilt angles ⁇ in the second embodiment are 25° and 35°, respectively, and the convex surface 125 accounts for 60% of the total length of the blade.
  • the angle ⁇ of the leading edge surface 121 with respect to the central axis is 60°, and the height of the leading edge surface.
  • the impeller in the comparative example was identical to the basic structure and parameters of the impeller of the present invention, except that the impeller in the comparative example was a flat blade.

Landscapes

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

Abstract

L'invention concerne une roue (100), un ventilateur et un moteur, la roue (100) comprenant un moyeu approximativement conique (11) et une pluralité de pales (12), disposées à des intervalles le long d'une direction circonférentielle sur une surface périphérique du moyeu (11). Les pales comprennent une surface de bord avant (121) au niveau d'une extrémité d'entrée et une surface de bord arrière (122) au niveau d'une extrémité de sortie. Les pales sont des plaques plates qui ont été torsadées. Des sections de bord arrière des pales sont torsadées par rapport à une direction circonférentielle et forment des pentes.
PCT/CN2017/113990 2017-07-03 2017-11-30 Roue, ventilateur et moteur WO2019006971A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
KR1020197031208A KR20190125501A (ko) 2017-07-03 2017-11-30 임펠러, 팬 및 모터
JP2019560378A JP2020518761A (ja) 2017-07-03 2017-11-30 インペラ、ファン及びモータ

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CN201720799224.2 2017-07-03
CN201720799224.2U CN206874553U (zh) 2017-07-03 2017-07-03 叶轮、风机和电机
CN201710531117.6A CN107143523A (zh) 2017-07-03 2017-07-03 叶轮、风机和电机
CN201710531117.6 2017-07-03

Publications (1)

Publication Number Publication Date
WO2019006971A1 true WO2019006971A1 (fr) 2019-01-10

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Application Number Title Priority Date Filing Date
PCT/CN2017/113990 WO2019006971A1 (fr) 2017-07-03 2017-11-30 Roue, ventilateur et moteur

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JP (1) JP2020518761A (fr)
KR (1) KR20190125501A (fr)
WO (1) WO2019006971A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR102338013B1 (ko) * 2020-08-31 2021-12-10 아륭기공(주) 탈포기능이 구비된 쿨런트 펌프
JP2023067008A (ja) * 2021-10-29 2023-05-16 三星電子株式会社 インペラおよびこれを用いた掃除機

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015071972A (ja) * 2013-10-03 2015-04-16 株式会社Ihi 遠心圧縮機
JP2016037901A (ja) * 2014-08-07 2016-03-22 日立金属株式会社 羽根車
EP3037194A1 (fr) * 2014-12-22 2016-06-29 Robert Bosch Gmbh Roue de turbine et son procede de fabrication
CN106382254A (zh) * 2016-11-23 2017-02-08 广东威灵电机制造有限公司 叶轮
CN107143523A (zh) * 2017-07-03 2017-09-08 广东威灵电机制造有限公司 叶轮、风机和电机
CN107143522A (zh) * 2017-07-03 2017-09-08 广东威灵电机制造有限公司 叶轮、风机和电机
CN206874554U (zh) * 2017-07-03 2018-01-12 广东威灵电机制造有限公司 叶轮、风机和电机

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999036701A1 (fr) * 1998-01-14 1999-07-22 Ebara Corporation Turbomachines centrifuges
JP4888436B2 (ja) * 2007-08-03 2012-02-29 株式会社日立プラントテクノロジー 遠心圧縮機とその羽根車およびその運転方法
JP5879103B2 (ja) * 2011-11-17 2016-03-08 株式会社日立製作所 遠心式流体機械

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015071972A (ja) * 2013-10-03 2015-04-16 株式会社Ihi 遠心圧縮機
JP2016037901A (ja) * 2014-08-07 2016-03-22 日立金属株式会社 羽根車
EP3037194A1 (fr) * 2014-12-22 2016-06-29 Robert Bosch Gmbh Roue de turbine et son procede de fabrication
CN106382254A (zh) * 2016-11-23 2017-02-08 广东威灵电机制造有限公司 叶轮
CN107143523A (zh) * 2017-07-03 2017-09-08 广东威灵电机制造有限公司 叶轮、风机和电机
CN107143522A (zh) * 2017-07-03 2017-09-08 广东威灵电机制造有限公司 叶轮、风机和电机
CN206874554U (zh) * 2017-07-03 2018-01-12 广东威灵电机制造有限公司 叶轮、风机和电机

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Publication number Publication date
JP2020518761A (ja) 2020-06-25
KR20190125501A (ko) 2019-11-06

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