WO2021139508A1 - 扩压器、送风装置及吸尘设备 - Google Patents

扩压器、送风装置及吸尘设备 Download PDF

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Publication number
WO2021139508A1
WO2021139508A1 PCT/CN2020/137650 CN2020137650W WO2021139508A1 WO 2021139508 A1 WO2021139508 A1 WO 2021139508A1 CN 2020137650 W CN2020137650 W CN 2020137650W WO 2021139508 A1 WO2021139508 A1 WO 2021139508A1
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WO
WIPO (PCT)
Prior art keywords
row
blades
stationary
stationary blades
blade
Prior art date
Application number
PCT/CN2020/137650
Other languages
English (en)
French (fr)
Inventor
张伟
蒋婷婷
周亚运
杨帆
吕琢
Original Assignee
广东威灵电机制造有限公司
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 CN202010010950.8A external-priority patent/CN113074138B/zh
Priority claimed from CN202010010952.7A external-priority patent/CN113074140B/zh
Priority claimed from CN202010011558.5A external-priority patent/CN113074142B/zh
Application filed by 广东威灵电机制造有限公司 filed Critical 广东威灵电机制造有限公司
Priority to KR1020227016870A priority Critical patent/KR20220079992A/ko
Priority to JP2022529913A priority patent/JP7407931B2/ja
Priority to EP20911796.9A priority patent/EP4050222A4/en
Publication of WO2021139508A1 publication Critical patent/WO2021139508A1/zh
Priority to US17/829,872 priority patent/US20220290689A1/en
Priority to JP2023106404A priority patent/JP2023115279A/ja
Priority to JP2023106405A priority patent/JP2023115280A/ja

Links

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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F04D29/444—Bladed diffusers
    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47L—DOMESTIC WASHING OR CLEANING; SUCTION CLEANERS IN GENERAL
    • A47L5/00—Structural features of suction cleaners
    • A47L5/12—Structural features of suction cleaners with power-driven air-pumps or air-compressors, e.g. driven by motor vehicle engine vacuum
    • A47L5/22—Structural features of suction cleaners with power-driven air-pumps or air-compressors, e.g. driven by motor vehicle engine vacuum with rotary 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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/16—Centrifugal pumps for displacing without appreciable compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/16—Centrifugal pumps for displacing without appreciable compression
    • F04D17/165—Axial entry and discharge
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings
    • F04D29/4253—Fan casings with axial entry and discharge
    • 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
    • F04D29/70—Suction grids; Strainers; Dust separation; Cleaning
    • F04D29/701—Suction grids; Strainers; Dust separation; Cleaning especially adapted for elastic fluid pumps
    • F04D29/703—Suction grids; Strainers; Dust separation; Cleaning especially adapted for elastic fluid pumps specially for fans, e.g. fan guards
    • 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
    • F05D2240/10—Stators
    • F05D2240/12—Fluid guiding means, e.g. vanes
    • 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
    • F05D2240/10—Stators
    • F05D2240/12—Fluid guiding means, e.g. vanes
    • F05D2240/129—Cascades, i.e. assemblies of similar profiles acting in parallel

Definitions

  • This application belongs to the technical field of cleaning equipment, and in particular relates to a diffuser, an air supply device and a dust suction device.
  • the dust suction equipment is usually equipped with an air supply device, and a diffuser is installed in the air supply device to convert the kinetic energy of the airflow flowing through the air supply device into pressure energy, thereby reducing the flow loss of the airflow.
  • the diffuser is usually provided with static vanes to guide and pressurize the airflow.
  • the purpose of this embodiment is to provide a diffuser, which aims to solve the technical problem of large flow loss when the air flows through the diffuser in the prior art.
  • a diffuser including a base ring member and a plurality of rows of stationary blades, each row of the stationary blades is sequentially arranged on the outer ring wall of the base ring member along the axial direction of the base ring member , And are arranged along the circumferential direction of the base ring member, the opposite sides of the base ring member along the axial direction are respectively the air inlet side and the air outlet side, from the air inlet side to the air outlet side , Wherein the chord length of one row of the stationary blades is greater than or equal to the chord length of the next row of the stationary blades adjacent to the row of the stationary blades;
  • the stationary blades have an installation angle, from the inlet side to the outlet side, wherein the installation angle of one row of the stationary blades is less than or equal to the next row of the stationary blades adjacent to the row of stationary blades.
  • the installation angle of the blade is less than or equal to the next row of the stationary blades adjacent to the row of stationary blades.
  • the second aspect Provide a diffuser, including a base ring member and a plurality of stationary blades, the plurality of stationary blades are arranged in multiple rows along the axial direction of the base ring member, and each row of the stationary blades The number of stationary blades is multiple, and a plurality of stationary blades in each row of stationary blades are arranged along the circumference of the base ring member, and the cross section of the base ring member is circular; at least one row of the plurality of rows of the stationary blades The profile of each of the stationary blades is inclined to one side of the stationary blade.
  • the third aspect Provide a diffuser, including a base ring member and a plurality of stationary blades, the plurality of stationary blades are arranged in multiple rows along the axial direction of the base ring member, and each row of the stationary blades
  • the number of stationary blades is multiple, and a plurality of stationary blades in each row of stationary blades are arranged along the circumference of the base ring member, and the cross section of the base ring member is circular; at least one row of the plurality of rows of the stationary blades
  • the thickness of each of the stationary blades is set non-constantly from the head to the tail of the stationary blade.
  • the fourth aspect Provides an air supply device, including the above-mentioned diffuser.
  • a dust suction device including the above-mentioned air blowing device.
  • the diffuser provided in this embodiment has multiple rows of stationary blades arranged in the diffuser along the axial direction of the base ring, so that the airflow through the diffuser can be obtained
  • the multi-stage drainage effect of each row of stator blades realizes the multi-stage deceleration and pressurization of the airflow, thereby reducing the flow loss caused by the airflow when flowing through the diffuser.
  • the air supply device provided in this embodiment includes the above-mentioned diffuser, and the above-mentioned diffuser can ensure that the airflow can be smoothly realized without large flow loss when flowing through the diffuser. Decelerate and pressurize. In this way, the overall working efficiency of the air supply device is also improved, and the working energy consumption of the air supply device is saved.
  • the dust collection equipment provided by this embodiment includes the above-mentioned air supply device, and the above-mentioned air supply device can achieve smoother deceleration and pressure increase of the air flow, and is energy-saving and environmentally friendly during operation. This also significantly improves the inclusion of the above-mentioned air supply device. The dust collection effect of the dust collection equipment of the air supply device also saves the working energy consumption of the dust collection equipment.
  • Figure 1 is a schematic diagram of the structure of the air supply device provided by this embodiment
  • Figure 2 is a schematic diagram of the structure of the diffuser of the air supply device provided by this embodiment
  • Figure 3 is a cascade diagram of the first row of stationary blades of the diffuser of the air supply device provided by this embodiment
  • FIG. 4 is a cascade diagram of the first row of stationary blades and the second row of stationary blades of the diffuser of the air supply device provided by this embodiment;
  • Figure 5 is a schematic structural view of the base ring of the diffuser of the air supply device provided by this embodiment
  • Fig. 6 is a schematic diagram of a three-dimensional structure of a diffuser provided by an embodiment of the application.
  • Fig. 7 is a schematic plan view of the cascade of the diffuser of Fig. 6;
  • Fig. 8 is a schematic front view of the structure of the diffuser of Fig. 6;
  • Fig. 9 is a schematic top view of the base ring and the second row of stationary blades in the diffuser of Fig. 8;
  • Fig. 10 is a schematic bottom view of the base ring and the second row of stationary blades in the diffuser of Fig. 8;
  • Fig. 11 is a schematic cross-sectional structure view taken along line A-A in Fig. 8;
  • FIG. 12 is a schematic sectional view of the base ring member and a row of stator blades along the radial surface of the base ring member in the diffuser provided by the embodiment of the application;
  • FIG. 13 is a schematic diagram of a stationary blade on a meridian projection surface in a diffuser provided by an embodiment of the application;
  • FIG. 14 is a schematic sectional view of the diffuser along the axis passing through the base ring according to the embodiment of the application;
  • 15 is a schematic cross-sectional structure diagram of the first air supply device provided by an embodiment of the application.
  • FIG. 16 is a schematic cross-sectional structure diagram of a second type of air blowing device provided by an embodiment of the application.
  • first and second are only used for descriptive purposes, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of indicated technical features. Thus, the features defined with “first” and “second” may explicitly or implicitly include one or more of these features. In the description of the present application, “multiple” means two or more than two, unless otherwise specifically defined.
  • the terms “installed”, “connected”, “connected”, “fixed” and other terms should be understood in a broad sense, for example, it can be a fixed connection or a detachable connection , Or integrated; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the internal communication of two components or the interaction relationship between two components.
  • installed can be a fixed connection or a detachable connection , Or integrated; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the internal communication of two components or the interaction relationship between two components.
  • this embodiment provides a diffuser 10 for an air blowing device 20, which can be, but is not limited to, used for dust collection equipment.
  • the diffuser 10 includes a base ring member 11 and a plurality of rows of stationary blades 114, and each row of stationary blades 114 is sequentially arranged on the outer ring wall 111 of the base ring member 11 along the axial direction of the base ring member 11.
  • the opposite sides of the base ring 11 along its axial direction are the air inlet side and the air outlet side
  • the base ring 11 has an outer ring wall 111 and an inner ring
  • a number of mounting holes 113 are opened in the wall 112 and the inner ring wall 112, and the base ring member 11 passes through the mounting hole 113 and the frame 221 through a locking bolt to achieve a fixed connection in the diffuser 10.
  • the chord length of one row of stationary blades 114 is greater than or equal to the chord length of the next row of stationary blades 114 adjacent to the row of stationary blades 114.
  • the stationary blades 114 have an installation angle, from the inlet side to the outlet side, the installation angle of one row of stationary blades 114 is smaller than or equal to the installation angle of the next row of stationary blades 114 adjacent to the row of stationary blades 114.
  • the connecting line of the corresponding points of the heads of multiple stator blades 114 in the same row is called the forehead line (shown by L1 in Fig. 3);
  • the back forehead line the connecting line of the corresponding points of the tails of the multiple stationary blades 114 in the same row is called the back forehead line (shown by L2 in Fig. 3);
  • Entrance placement angle the angle formed by the midline and the tangent line of the forehead line at the head of the blade (shown as ⁇ in Figure 3);
  • Exit placement angle the angle formed by the tangent line between the midline and the forehead line at the tail of the blade (shown as ⁇ in Figure 3);
  • Installation angle refers to the angle between the forehead line of the stator blade 114 and the chord length, which changes with the chord length (shown by ⁇ in Figure 3);
  • the head of the stationary blade 114 along the axial direction of the base ring 11, the foremost position of the stationary blade 114 is the head (shown in a in Fig. 3);
  • the tail of the stationary blade 114 along the axial direction of the base ring 11, the final position of the stationary blade 114 is the tail (shown in b in Figure 3);
  • the height of the stationary blade 114 the length of the stationary blade 114 in the radial direction of the base ring 11;
  • Tip The position where the stationary blade 114 increases to the top along its radial direction is the tip;
  • Chord length the straight line distance between the center line between the head of the stationary blade 114 and the tail of the stationary blade 114 is the chord length (shown by L4 in Fig. 3);
  • Centerline The curve formed by connecting each midpoint in the thickness direction of the stationary blade 114 from the head to the tail of the stationary blade 114 is called the centerline (shown by L3 in FIG. 3).
  • multiple rows of stator blades 114 are arranged in the diffuser along the axial direction of the base ring member, so that the airflow passing through the diffuser can obtain the multi-stage drainage of each row of stator blades 114 In this way, the multi-stage deceleration and pressurization of the air flow is realized, thereby reducing the flow loss caused by the air flow when it flows through the diffuser.
  • the diffuser 10 provided in this embodiment has multiple rows of stator blades 114 arranged in the diffuser 10 along the axial direction of the base ring 11, so that the flow
  • the airflow passing through the diffuser 10 can obtain the multi-stage drainage effect of each row of stator blades 114, so that the multi-stage deceleration and supercharging of the airflow is firstly realized.
  • the chord length of one row of stationary blades 114 is greater than or equal to the chord length of the next row of stationary blades 114 adjacent to the row of stationary blades 114 from the inlet side to the outlet side of the base ring 11.
  • each row of static blades 114 can gradually reduce the flow separation phenomenon caused by the airflow, and significantly reduce the flow loss caused by the airflow when flowing through the diffuser 10. In this way, the air flow can be smoothly decelerated and pressurized under the guiding action of each row of stator blades 114 without causing a large flow loss.
  • the head of the stationary blade 114 has an inlet placement angle from the inlet side to the outlet side.
  • the inlet placement angle of a row of stationary blades 114 is less than or equal to the next adjacent row of stationary blades 114.
  • the entrance of the discharging vane 114 is placed at an angle.
  • the outlet placement angle of one row of stationary blades 114 is less than or equal to the outlet placement angle of the next row of stationary blades 114 adjacent to the row of stationary blades 114.
  • the outlet placement angle of one row of stationary blades 114 is less than or equal to the outlet of the next row of stationary blades 114
  • the angle is placed, which further effectively suppresses the unevenness of the air flow when flowing from the upper row of stationary blades 114 to the next row of stationary blades 114, and also effectively suppresses the flow of air flow from the upper row of stationary blades 114 to the next row.
  • the flow separation phenomenon generated by the stator blades 114 effectively reduces the flow loss caused by the air flow from the upper row of the stator blades 114 to the next row of the stator blades 114, and improves the air flow efficiency.
  • the tail of the stationary blade 114 has an outlet placement angle, from the inlet side to the outlet side.
  • the outlet placement angle of one row of stationary blades 114 may be less than or equal to the next adjacent row of stationary blades 114.
  • the entrance of the discharging vane 114 is placed at an angle. This allows the airflow to flow smoothly from the upper row of stationary blades 114 to the next row of stationary blades 114.
  • the outlet placement angle of one row of stationary blades 114 may also be greater than the inlet placement angle of the next row of stationary blades 114 adjacent to the row.
  • the diffuser 10 includes a first row of stationary blades 12 and a second row of stationary blades 13, the first row of stationary blades 12 and the second row of stationary blades 13 from the inlet side to the outlet
  • the wind side is sequentially arranged on the outer ring wall 111 of the base ring 11 along the axial direction of the base ring 11.
  • the number of rows of the stator blades 114 can be two rows, which on the one hand ensures that there are a sufficient number of the stator blades 114 to fully divert and diffuse the airflow, and on the other hand, it also ensures that the number of rows of the stator blades 114 will not Too much, thereby achieving a compact design of the diffuser 10.
  • the angle value of the inlet placement angle of the first row of stationary blades 12 is 5°-20°
  • the angle value of the inlet placement angle of the second row of stationary blades 13 is 20°-40°.
  • the angle value of the inlet placement angle of the first row of stationary blades 12 may be 5°, 5.5°, 6°, 6.5°, 7°, 7.5°, 8°, 8.5°, 9°, 9.5°, 10° , 10.5°, 11°, 11.5°, 12°, 12.5°, 13°, 13.5°, 14°, 14.5°, 15°, 15.5°, 16°, 16.5°, 17°, 17.5°, 18°, 18.5 °, 19°, 19.5 or 20°.
  • the angle value of the inlet placement angle of the second row of stationary blades 13 can be 20°, 20.5°, 21°, 21.5°, 22°, 22.5°, 23°, 23.5°, 24°, 24.5°, 25°, 25.5° , 26°, 26.5°, 27°, 27.5°, 28°, 28.5°, 29°, 29.5°, 30°, 30.5°, 31°, 31.5°, 32°, 32.5°, 33°, 33.5°, 34 °, 34.5, 35°, 35.5°, 36°, 36.5°, 37°, 37.5°, 38°, 38.5°, 39°, 39.5° or 40°.
  • the angle value of the outlet placement angle of the first row of stationary blades 12 is 10°-60°, and the angle value of the inlet placement angle of the second row of stationary blades 13 is 60°-80°.
  • the angle value of the outlet placement angle of the first row of stationary blades 12 may be 10°, 15°, 20°, 25°, 30°, 35°, 40°, 45°, 50°, 55° or 60° .
  • the angle value of the inlet placement angle of the second row of stationary blades 13 can be 60°, 61°, 62°, 63°, 64°, 65°, 66°, 67°, 68°, 69°, 70°, 71° , 72°, 73°, 74°, 75°, 76°, 77°, 78°, 79° or 80°.
  • the ratio of the chord length of the first row of stationary blades 12 to the chord length of the second row of stationary blades 13 is greater than or equal to 1 and less than or equal to 5.
  • the ratio of the chord length of the first row of stationary blades 12 to the chord length of the second row of stationary blades 13 can be 1, 1.2, 1.5, 1.7, 2, 2.2, 2.5, 2.7, 3, 3, 3.2, 3.5, 3.7, 4, 4.2, 4.5, 4.7 or 5.
  • the number of blades of the first row of stationary blades 12 is less than or equal to the number of blades of the second row of stationary blades 13, and the first row of stationary blades 12 and the second row of stationary blades 13 respectively extend uniformly in the circumferential direction of the outer ring wall
  • the first row of stationary blades 12 and the second row of stationary blades 13 are mutually offset in the axial direction of the outer ring wall, and at least the head or tail of one stationary blade 114 in the first row of stationary blades 12 and the second row of stationary blades
  • the head or tail of one of the stationary blades 114 in 13 is aligned with the axial direction of the outer ring wall. In this way, the cohesion between the first row of stationary blades 12 and the second row of stationary blades 13 is stronger, thereby facilitating the efficient flow of airflow from the first row of stationary blades 12 to the second row of stationary blades 13.
  • the number of blades of the first row of stationary blades 12 is 6 to 20, and the number of blades of the second row of stationary blades 13 is 10 to 30.
  • the number of blades of the first row of stator blades 12 can be 6, 7, 8, 9, 10, 11, 12, 13, 14, 15, 16, 17, 18, 19 or 20 blades
  • the number of blades of the second row of stator blades 13 can be 10, 11, 12, 13, 14, 15, 16, 17, 18, 19, 20 pieces, 21 pieces, 22 pieces, 23 pieces, 24 pieces, 25 pieces, 26 pieces, 27 pieces, 28 pieces, 29 pieces or 30 pieces.
  • the first row of stationary blades 12 and the second row of stationary blades 13 do not correspond one-to-one, and it is not a strict N-to-one relationship. Instead, the number of the second row of stationary blades 13 is determined first. Position a certain end of the stationary blade 114 in the second row of stationary blades 13 and a certain end of the stationary blade 114 in the first row of stationary blades 12, and then evenly distribute the second row of stationary blades 13 on the base ring member 11 On the outer ring wall, after the layout of the second row of stationary blades 13 is completed, the layout of the first row of stationary blades 12 is performed.
  • the distance between the head of the first row of stationary blades 12 and the tail of the second row of stationary blades 13 in the axial direction of the base ring member 11 (shown in D in FIG. 4) Less than or equal to 3mm.
  • this ensures that the first row of stationary blades 12
  • the smooth connection with the second row of stationary blades 13 to the airflow ensures the flow efficiency of the airflow.
  • the distance between the heads of the first row of stationary blades 12 and the tails of the second row of stationary blades 13 along the axial direction of the base ring member 11 is greater than or equal to 1 mm and less than or equal to 3 mm.
  • the air flow is ensured.
  • the best balance between flow efficiency and avoiding interference between the first row of stationary blades 12 and the second row of stationary blades 13 is achieved, so that the first row of stationary blades 12 and the second row of stationary blades 13 can avoid mutual interference.
  • the airflow passing through the first row of stationary blades 12 and the second row of stationary blades 13 achieves optimal drainage and diffusion effects.
  • the outlet placement angle includes a first outlet placement angle at the root of the stationary blade 114 and a second outlet placement angle at the tip of the stationary blade 114.
  • the angle value of the first outlet placement angle and the first outlet placement angle The difference between the angle values of the two outlet installation angles is 0° ⁇ 20°.
  • the contour line of the stator blade 114 along the radial direction of the base ring 11 is a curve, indicating the static
  • the blade 114 is bent in the radial direction of the base ring member 11.
  • the difference between the angle value of the first outlet angle and the angle value of the second outlet angle may be 0°, 1°, 2°, 3°, 4°, 5°, 6°, 7°, 8. °, 9°, 10°, 11°, 12°, 13°, 14°, 15°, 16°, 17°, 18°, 19° or 20°.
  • the stationary blade 114 is an arc-shaped blade. Specifically, by setting the stator blade 114 as an arc-shaped blade, the stator blade 114 has a smoother and smoother drainage curve, thereby ensuring that the airflow can flow through the stator blade 114 more smoothly and stably.
  • each stator blade 114 of the diffuser 10 abuts against the inner side wall of the windshield 21. Specifically, by making the top surface of each stator blade 114 abut against the inner side wall of the wind hood 21, each stator blade 114 can fully occupy the area enclosed by the base ring 11 and the wind hood 21, thereby realizing the alignment.
  • the airflow entering the air blowing device 20 achieves a sufficient drainage effect, and thereby achieves sufficient diffusion and deceleration of the airflow.
  • the inlet placement angle of the first row of stationary blades 12 is 15°
  • the outlet placement angle is 24°
  • the second row of stationary blades 13 The entrance angle is 35°
  • the exit angle is 75°
  • the axial distance between the tail of the first row of stationary blades 12 and the head of the corresponding second row of stationary blades 13 is 1.8mm.
  • the inlet placement angle of the first row of stationary blades 12 is 20°
  • the outlet placement angle is 27°
  • the inlet placement angle of the second row of stationary blades 13 is 42°
  • the outlet placement angle is 60°
  • the axial distance between the tail of the first row of stationary blades 12 and the head of the corresponding second row of stationary blades 13 is 1.3mm.
  • This embodiment also provides an air blowing device 20, which includes the above-mentioned diffuser 10.
  • the air blowing device 20 includes a wind hood 21, a driving mechanism 22, a moving impeller 23, and a diffuser 10.
  • the driving mechanism 22 is arranged in the wind hood 21, and the moving impeller 23 and the driving mechanism 22 are connected and correspond to the wind hood 21.
  • the air inlet 24 is provided, and the diffuser 10 is fixed in the wind hood 21 and is located on the side of the moving impeller 23 away from the air inlet 24.
  • the driving mechanism 22 includes a frame 221, a motor 222, and a circuit board 223.
  • the frame 221 and the circuit board 223 are both fixed in the windshield 21, the motor 222 is arranged on the frame 221, and the drive shaft 224 of the motor 222 passes through
  • the passing frame 221 and the diffuser 10 are connected with the moving impeller 23 to drive the moving impeller 23 to rotate.
  • the air supply device provided in this embodiment includes the above-mentioned diffuser, and the above-mentioned diffuser can ensure that the airflow can be smoothly realized without large flow loss when flowing through the diffuser. Decelerate and pressurize. In this way, the overall working efficiency of the air supply device is also improved, and the working energy consumption of the air supply device is saved.
  • This embodiment also provides a dust suction device, which includes the above-mentioned air blowing device.
  • the dust collection equipment provided by this embodiment includes the above-mentioned air supply device, and the above-mentioned air supply device can achieve smoother deceleration and pressure increase of the air flow, and is energy-saving and environmentally friendly during operation. This also significantly improves the inclusion of the above-mentioned air supply device.
  • the dust collection effect of the dust collection equipment of the air supply device also saves the working energy consumption of the dust collection equipment.
  • the diffuser 10 includes a base ring 11 and a plurality of stationary blades 114, the plurality of stationary blades 114 are arranged in multiple rows, and the multiple rows of static blades
  • the blades 114 are arranged along the axial direction of the base ring 11, the number of stationary blades 114 in each row of stationary blades 114 is multiple, and the multiple stationary blades 114 in each row of stationary blades 114 are arranged along the circumferential direction of the base ring 11;
  • a flow channel 15 for guiding the flow of air flow may be formed between the two stationary blades 114.
  • the cross section of the base ring member 11 is circular, so that when the air flow is deflected toward the base ring member 11 to rotate radially and flow along the axis of the base ring member 11, the flow to the peripheral side of the base ring member 11 is close to each other, so that it is subject to resistance. It is similar, so that the airflow flows more smoothly to the peripheral side of the base ring 11, and energy loss is reduced.
  • the multiple stator blades 114 are arranged in multiple rows along the axial direction of the base ring 11, and the multiple rows of stator blades 114 can gradually guide the air flow, reduce energy loss, and improve the pressure diffusion effect.
  • the definition is as follows: when air flows through the diffuser 10, the direction of the air inlet is upward, forward, or head, and the direction of the air outlet is downward, rear, or tail.
  • a plurality of stationary blades 114 are divided into two rows along the axial direction of the base ring 11, from top to bottom, there are the first row of stationary blades 12 and the second row of stationary blades 13, that is, the first row of stationary blades 12 It is the upper row of the second row of stationary blades 13, and the second row of stationary blades 13 is the next row of the first row of stationary blades 12.
  • the plurality of stationary blades 114 are divided into three rows along the axial direction of the base ring 11, from top to bottom, there are a first row of stationary blades 12, a second row of stationary blades 13, and a third row of stationary blades 114.
  • the plurality of stationary blades 114 are divided into four or more rows along the axial direction of the base ring member 11, and from top to bottom are the first row of stationary blades 12, the second row of stationary blades 13, and the third row of stationary blades 114... . That is, when a plurality of stator blades 114 are arranged in N (N is a positive integer, N ⁇ 2) rows along the axis of the base ring 11, they are divided into the first row, the second row...the Nth row from top to bottom; ,
  • the M-1 row of stationary blades 114 is the upper row of stationary blades 114 of the M-th row of stationary blades 114, and the M-th row of stationary blades 114 is the next row of stationary blades 114 of the M-1 row of stationary blades 114, (M is Positive integer, M ⁇ N).
  • the profile 18 of the stationary blade 114 refers to the two side surfaces between the root 17 and the tip 16 of the stationary blade 114; the two side surfaces between the root 17 and the tip 16 of the stationary blade 114 are respectively The suction surface 19 and the pressure surface 14 are collectively referred to as the profile 18; and the blade root 17 of the stationary blade 114 refers to the position of the stationary blade 114 close to the root of the base ring member 11; the blade of the stationary blade 114
  • the tip 16 refers to the position of the stator blade 114 that is far away from the top of the base ring member 11; the head of the stator blade 114 refers to the position at the front end of the stator blade 114 along the air flow direction, that is, the position on the stator blade 114 that starts to contact the air flow; the stator blade 114
  • the tail of refers to the part located at the rear end of the stationary blade 114 along the flow direction of the airflow, that is, the part on the corresponding stationary blade 114 when the airflow leaves
  • each stationary blade 114 in the first row of stationary blades 12: the two side surfaces of each stationary blade 114 are suction surface 19a and pressure surface 14a respectively, and the suction surface 19a and pressure surface 14a are collectively referred to as the profile 18a of the stationary blade 114; A flow channel 15a for guiding the airflow can be formed between two adjacent stator blades 114.
  • the two sides of each stationary blade 114 are suction surface 19b and pressure surface 14b, respectively.
  • the suction surface 19b and pressure surface 14b are collectively referred to as the profile 18b of the stationary blade 114; two adjacent stationary blades
  • a flow channel 15b for guiding the air flow may be formed between 114.
  • a plurality of stator blades 114 are divided into two rows along the axial direction of the base ring member 11. From top to bottom, there are the first row of stator blades 12 and the second row of stator blades 13, namely, the first row of stator blades 12 and the second row of stator blades 13.
  • One row of stationary blades 12 is the upper row of the second row of stationary blades 13, and the second row of stationary blades 13 is the next row of the first row of stationary blades 12.
  • the plurality of stator blades 114 are divided into three, four or more rows along the axial direction of the base ring 11.
  • a curved surface of equal unit thickness with the same shape as the base ring 11 is cut at the middle of the height direction of the stator blade 114.
  • the curved surface is cylindrical, and the curved surface is coaxial with the base ring 11.
  • the curved surface is expanded in a plane, and a plane cascade diagram of each stationary blade 114 is obtained.
  • the connecting line at the corresponding point of the head of each stationary blade 114 in each row of stationary blades 114 is called the forehead line L1 of the row of stationary blades 114
  • the forehead line L1 is the forehead line L1 of each stationary blade 114 in the row of stationary blades 114.
  • the tangent line of the corresponding point of the head; the connecting line of the corresponding point of the tail of each stationary blade 114 in each row of stationary blades 114 is called the rear forehead line L2 of the row of stationary blades 114, and the rear forehead line L2 is the row of stationary blades 114.
  • the tangent line of the corresponding point at the tail of the blade 114; the curve formed by the midpoints of the thickness H of each stator blade 114 is called the center line L3 of the stator blade 114; the tangent line of the center line L3 at the head of the corresponding stator blade 114 corresponds to the head of the stator blade 114
  • the angle between the point tangent line is the entrance placement angle ⁇ , that is, the angle between the tangent line of the midline L3 at the head of the stator blade 114 and the corresponding forehead line L1 is the inlet placement angle ⁇ ;
  • the angle between the tangent to the corresponding point of the tail is the exit placement angle ⁇ , that is, the angle between the tangent of the midline L3 at the tail of the stationary blade 114 and the corresponding rear forehead line L2 is the outlet placement angle ⁇ ;
  • the midline L3 is between the head and the tail of the stationary blade 114
  • the distance between the two points is the chord length L4, and the
  • the connecting line of the corresponding point of the head of each stationary blade 114 in the first row of stationary blades 12 is the forehead line L1a of the first row of stationary blades 12, and the forehead line L1a is the first row of stationary blades.
  • the tangent line of the corresponding point of the head of each stationary blade 114 in the blade 12; the connecting line of the corresponding point of the tail of each stationary blade 114 in the first row of stationary blades 12 is the rear forehead line L2a of the first row of stationary blades 12, and the rear forehead line L2a Is the tangent line of the corresponding point of the tail of each stationary blade 114 in the first row of stationary blades 12;
  • the curve formed by the midpoint of the thickness Ha of each stationary blade 114 in the first row of stationary blades 12 is called the center line L3a of the stationary blade 114;
  • the angle between the center line L3a of each stationary blade 114 in the row of stationary blades 12 at the tangent to the head of the stationary blade 114 and the tangent to the corresponding point of the head of the stationary blade 114 is the entrance placement angle ⁇ a; each stationary blade in the first row of stationary blades 12
  • the connecting line of the corresponding points of the heads of the stationary blades 114 in the second row of stationary blades 13 is the forehead line L1b of the second row of stationary blades 13, and the forehead line L1b is the second row of stationary blades.
  • the tangent line of the corresponding point of the head of each stationary blade 114 in the blade 13; the connecting line of the corresponding point of the tail of each stationary blade 114 in the second row of stationary blades 13 is the rear forehead line L2b of the second row of stationary blades 13, and the rear forehead line L2b Is the tangent line of the corresponding point of the tail of each stationary blade 114 in the second row of stationary blades 13; the curve formed by the midpoints of the thickness Hb of each stationary blade 114 in the second row of stationary blades 13 is called the center line L3b of the stationary blade 114;
  • the angle between the center line L3b of each stationary blade 114 in the row of stationary blades 13 at the tangent line of the head of the stationary blade 114 and the tangent line of the corresponding point of the head of the stationary blade 114 is the entrance setting angle ⁇ b; each stationary blade in the second row of stationary blades 13 The angle between the centerline L3b of 114 at the tail of the stationary blade 114 and the
  • the thickness H of each stationary blade 114 in at least one row of stationary blades 114 is set non-constantly from the head to the tail of the stationary blade 114 Therefore, when the airflow enters the flow passage 15 between two adjacent stator blades 114 in the row of static blades 114, the flow separation is improved, and the flow separation loss is reduced; and the flow passage between the stator blades 114 in the row of stator blades 114 is flowed by the airflow.
  • the vortex flow can be improved, and the flow separation at the blade root 17 can be regulated; and when the air flow flows out of the flow channel 15 between the stator blades 114 in the row of the stator blades 114, the unevenness of the air flow can be reduced, the diffusion effect can be improved, and the aerodynamic noise can be reduced.
  • a plurality of rows of stationary blades 114 are arranged in the circumferential direction of the base ring 11, and the plurality of rows of stationary blades 114 gradually guide the airflow to reduce the absolute speed of the airflow to improve the supercharging effect; and at least one The thickness H of each stationary blade 114 in the stationary blade 114 is set non-constantly from the head to the tail of the stationary blade 114.
  • each stator blade 114 is inclined to the axial direction of the base ring member 11, and the length direction of each stator blade 114 refers to the direction in which the head and the tail of the stator blade 114 are connected.
  • the flow path 15 between the blades 114 can gradually guide the airflow to change direction and reduce the energy loss of the airflow.
  • the thickness H of each stationary blade 114 in one of the rows of stationary blades 114 can be set non-constantly from the head to the tail of the stationary blade 114.
  • the thickness H of each stationary blade 114 in the rows of stationary blades 114 may be set non-constantly from the head to the tail of the stationary blade 114. It is also possible to set the thickness H of each stationary blade 114 in each row of stationary blades 114 non-constantly from the head to the tail of the stationary blade 114.
  • each stationary blade 114 with a non-constant thickness H the thickness H of each stationary blade 114 first gradually increases from the head to the tail of the stationary blade 114 and then gradually decreases, so that the airflow passes through the stationary blades.
  • the flow passage 15 between the blades 114 first gradually reduce the circumferential velocity and absolute velocity of the air flow to reduce the flow separation loss; then improve the vortex, reduce the unevenness of the flow passage 15 between the air flow out of the stator blades 114, reduce the flow separation loss, and improve Diffuser effect reduces aerodynamic noise.
  • the chord length L5 at the position where the thickness H of each stator blade 114 is the largest is 30 of the chord length L of the stator blade 114 % ⁇ 45%, that is, in the thickness H corresponding to each point on the centerline of each stator blade 114, the chord length L5 of the position corresponding to the point on the centerline where the thickness H is the largest is 30% ⁇ 45% of the chord length L of the stator blade 114;
  • each position on the center line of each stationary blade 114 in the row of stationary blades 114 corresponds to the thickness Ha
  • the position chord length L5a of the point corresponding to the maximum Ha is 30%-45% of the chord length La of the stator blade 114.
  • each position on the center line of each stationary blade 114 in the row of stationary blades 114 corresponds to the thickness Hb.
  • the chord length L5b of the position corresponding to the point where Hb is the largest is 30%-45% of the chord length Lb of the stator blade 114.
  • the chord length L5 at the position where the thickness H of each stator blade 114 is the largest is 35 of the chord length L of the stator blade 114 % ⁇ 40%, that is, in the thickness H corresponding to each point on the centerline of each stator blade 114, the chord length L5 of the position corresponding to the point on the centerline where the thickness H is the largest is 35%-40% of the chord length L of the stator blade 114; Reduce the flow separation loss, improve the eddy current, improve the pressure diffusion effect, and reduce the aerodynamic noise.
  • the thickness Hb of each stationary blade 114 satisfies the following relationship, that is, in the second row of stationary blades 13: each point on the center line of each stationary blade 114 corresponds to The thickness Hb satisfies the following relationship:
  • the thickness of the head of each stator blade 114 is in the range of 0.1-0.8mm;
  • chord length L5b at the position of each stator blade 114 is the thickness Hb at 40% of the chord length Lb of the stator blade 114 in the range of 1.1-1.4mm;
  • the thickness of the tail of each stationary blade 114 ranges from 0.1 to 1 mm.
  • the thickness Hb of each stationary blade 114 satisfies the following relationship, that is, in the second row of stationary blades 13: each point on the center line of each stationary blade 114 corresponds to The thickness Hb satisfies the following relationship:
  • the thickness of the head of each stator blade 114 is in the range of 0.1-0.8mm;
  • chord length L5b at the position of each stator blade 114 is 30% of the chord length Lb of the stator blade 114.
  • the thickness Hb ranges from 1 to 1.3 mm;
  • chord length L5b at the position of each stator blade 114 is the thickness Hb at 40% of the chord length Lb of the stator blade 114 in the range of 1.1-1.4mm;
  • chord length L5b at the position of each stator blade 114 is 50% of the chord length Lb of the stator blade 114.
  • the thickness Hb ranges from 1 to 1.3 mm;
  • chord length L5b at the position of each stator blade 114 is 60% of the chord length Lb of the stator blade 114.
  • the thickness Hb ranges from 0.9-1.2mm;
  • chord length L5b at the position of each stator blade 114 is 70% of the chord length Lb of the stator blade 114.
  • the thickness Hb is in the range of 0.8-1.1mm;
  • the thickness of the tail of each stationary blade 114 ranges from 0.1 to 1 mm.
  • T1 0.82+0.68L1b-0.17L1b 2 +0.011L1b 3 ;
  • T2 0.68L1b-0.17L1b 2 +0.011L1b 3 ;
  • L1b is the distance from the corresponding point on the centerline of the stationary blade 114 to the head of the stationary blade 114, that is, L1b is the position chord length of the corresponding point on the centerline of the stationary blade 114, L1b 2 is the square of L1b, and L1b 3 is the length of L1b.
  • T1 is the relational formula of the maximum thickness at the corresponding point on the centerline of the stator 114
  • T2 is the relational expression of the minimum thickness at the corresponding point on the center line of the stationary blade 114.
  • L1b is the static The distance from the corresponding point on the centerline of the blade 114 to the head of the stationary blade 114, that is, L1b is the chord length of the position of the corresponding point on the centerline of the stationary blade 114, L1b 2 is the square of L1b, L1b 3 is the third power of L1b, and 0.68L1b is 0.68 times L1b, 0.17L1b 2 is 0.17 times L1b 2 , and 0.011L1b 3 is 0.011 times L1b 3 .
  • the flow loss can be better reduced, the unevenness of the air flow is improved, the vortex flow is improved, the diffusion effect is
  • the outer diameter of the base ring 11 ranges from 35 to 80 mm. In this way, the thickness H of the stator blade 114 is better matched with the base ring 11, the size of the flow channel 15 between the adjacent stator blades 114 is ensured, the resistance to the air flow is reduced, the energy loss is reduced, and the pressure diffusion effect is improved.
  • any position on the center line of each stationary blade 114 corresponds to the thickness of the root 17 as H1, and the thickness at the tip 16 at this position is H2, H1 ⁇ H2, that is, the thickness H1 of the root 17 at any position on the center line of each stationary blade 114 is greater than or equal to the thickness H2 at the tip 16 of the position, to better control the flow separation near the blade root 17, reduce flow separation loss, and improve Diffuser effect.
  • the blade root 17 is thicker than the blade tip 16 or It is equal to 0.5mm, which is convenient for processing and manufacture, and ensures the strength of the tip 16 of each stator blade 114, and at the same time regulates the flow separation near the blade root 17, reduces the flow separation loss and improves the pressure diffusion effect.
  • each stationary blade 114 with a non-constant thickness H the thickness H at various locations on the center line of each stationary blade 114 gradually changes from the root 17 to the tip 16 of the stationary blade 114 Increase the setting to better control the flow separation near the blade root 17, reduce the flow separation loss, and improve the diffusion effect.
  • the airflow flows from the outlet of the moving impeller in a radial direction and flows in a high-speed circumferential direction, and turns into the diffuser 10 axially at a very short distance of the windshield, so the flow separation at the outlet of the moving impeller is serious.
  • each stator blade 114 is gradually increased from the head to the tail of the stator blade 114 to gradually reduce the circumferential velocity and absolute velocity of the airflow, and improve the deceleration and boost effect.
  • the vortex flow of the flow channel 15 can be further reduced, the energy loss is reduced, and the boosting effect is improved.
  • the installation angle ⁇ of the chord length L5 at different positions of the stator blade 114 is changed as follows: the installation angle ⁇ of the front half of the stator blade 114 is basically equal to the inlet installation angle ⁇ , so that the flow passage 15 between the first half of the stator blade 114 The area is evenly increased to achieve a uniform reduction in the absolute velocity of the airflow and the effect of boosting.
  • the installation angle ⁇ of the second half of the stator blade 114 is increased from the inlet placement angle ⁇ to the outlet placement angle ⁇ to reduce the circumferential velocity and absolute velocity of the airflow, and further improve the deceleration and boost effect.
  • the inlet setting angle ⁇ a of each stationary blade 114 ranges from 5 degrees to 10 degrees.
  • the setting angle ⁇ a of the inlet of each stator blade 114 is in the range of 5°-10°, which can better match the airflow with high circumferential velocity at the inlet of the stator blade 114, so as to uniformly reduce the absolute speed of the airflow and improve the supercharging effect.
  • the inlet setting angle ⁇ b of each stationary blade 114 ranges from 20 degrees to 60 degrees.
  • the setting angle ⁇ b of the inlet of each stator blade 114 is in the range of 20°-60°, which can better match the airflow with high circumferential velocity at the inlet of the stator blade 114, so as to uniformly reduce the absolute speed of the airflow and improve the supercharging effect.
  • the inlet setting angle ⁇ a of each stationary blade 114 ranges from 5 degrees to 10 degrees.
  • the inlet setting angle ⁇ b of each stationary blade 114 ranges from 20 degrees to 60 degrees.
  • the angle ⁇ a of the outlet of each stationary blade 114 ranges from 10 degrees to 20 degrees. As the airflow flows out from the tail of the stationary blade 114, the airflow angle distribution is more uneven. Setting the outlet angle ⁇ a in the range of 10 degrees to 20 degrees can further suppress the unevenness of the outlet flow at the tail of the stator blade 114, so as to reduce energy loss and improve the deceleration and boost effect.
  • the inlet setting angle ⁇ a of each stationary blade 114 ranges from 10 degrees to 20 degrees.
  • the inlet setting angle ⁇ b of each stationary blade 114 ranges from 20 degrees to 60 degrees.
  • the angle ⁇ b at the outlet of each stationary blade 114 ranges from 50° to 90°. As the airflow flows out from the tail of the stationary blade 114, the angular distribution of the airflow is more uneven. Setting the outlet angle ⁇ b in the range of 50 degrees to 90 degrees can further suppress the unevenness of the outlet flow at the tail of the stator blade 114, so as to reduce energy loss and improve the deceleration and boost effect.
  • the inlet setting angle ⁇ a of each stationary blade 114 ranges from 10 degrees to 20 degrees.
  • the inlet setting angle ⁇ b of each stationary blade 114 ranges from 50 degrees to 90 degrees.
  • the airflow can pass through the first row of stationary blades 12 to the second row of stationary blades 13, and the circumferential velocity and absolute velocity can be gradually reduced, reducing the unevenness of the airflow at the tail of the first row of stationary blades 12, and improving the supercharging effect.
  • the outlet setting angle ⁇ b of each stator blade 114 ranges from 60 degrees to 90 degrees
  • the inlet setting angle ka of each stator blade 114 ranges from 25 degrees to 50 degrees.
  • the inlet setting angle ⁇ of each stationary blade 114 varies less than or equal to 10 degrees along the radial direction of the base ring member 11, that is, the inlet setting angle ⁇ of each stationary blade 114 changes from the blade root 17 to the blade tip 16.
  • the amplitude is less than or equal to 10 degrees
  • the inlet placement angle ⁇ at the root 17 of each stationary blade 114 is greater than or equal to the inlet placement angle ⁇ at the tip 16 of the stationary blade 114, which can facilitate processing and manufacture on the one hand, and reduce it on the other hand.
  • the flow separation loss improves the pressure diffusion effect.
  • the number of stationary blades 114 in the next row of stationary blades 114 is 1.5 ⁇ the number of stationary blades 114 in the previous row of stationary blades 114 3 times.
  • the number of stator blades 114 in the previous row of stator blades 114 is relatively small, and the number of stator blades 114 in the next row of stator blades 114 is set to be larger, so that when the airflow passes through each row of stator blades 114 in turn, the airflow can be gradually strengthened. , Decelerate the air flow and improve the boosting effect.
  • the tail of each stationary blade 114 in the upper row of stationary blades 114 deviates from the adjacent next row along the circumferential direction of the base ring member 11
  • the head angle of the corresponding stationary blade 114 is less than or equal to 20 degrees.
  • the plane passing through the axis of the root 17 and the base ring 11 of each stator blade 114 in the upper row of stator blades 114, and passing through the root 17 and the base ring 11 of the head of the corresponding stator blade 114 in the next row The plane of the axis, the angle between the two planes is less than or equal to 20 degrees, so as to reduce the unevenness of the air flow, reduce the flow separation loss, and improve the boosting effect.
  • the inclination angle Q of the profile 18 at a certain point on the stator blade 114 refers to the radial direction of the base ring member 11 passing through the point on the stator blade 114 The angle between the line segment where the profile 18 of the stator blade 114 intersects the radial surface and the radial line passing through the point on the stator blade 114.
  • the radial surface of the base ring member 11 refers to a plane perpendicular to the axial direction of the base ring member 11, the radial line is the radial line of the base ring member 11, and the radial line of the base ring member 11 refers to the plane along the base ring member 11 11 A straight line extending in the radial direction, and a radial line passing through the point on the stator blade 114 refers to a straight line extending in the radial direction of the base ring member 11 and passing through the point.
  • the inclination angle of the head profile 18 of each stator blade 114 is greater than or equal to the inclination angle of the head profile 18 of the stator blade 114.
  • the inclination angle of the tail profile 18 of each stator blade 114 is set to be greater than or equal to the inclination angle of the head profile 18, so that when the air flows through the flow passage 15 between the stator blades 114, the stator blades 114 gradually strengthen the guidance and adjustment of the air flow to Improve the flow channel 15 vortex, reduce the separation loss, and then reduce the energy loss of the air flow and reduce the noise.
  • the inclination angle of the profile 18 of each stator blade 114 gradually increases from the head to the tail of the stator blade 114, so that when the air flows through
  • the airflow can be gradually adjusted to improve the airflow separation loss, reduce the energy loss, and reduce the noise.
  • the inclination angle of the head profile 18b of each stationary blade 114 is Q1
  • the inclination angle of the tail profile 18b of each stationary blade 114 is Q2 , Q2 ⁇ Q1.
  • the inclination angle Q1 of the tail profile 18b of each stator blade 114 in the second row of stator blades 13 is set to be greater than or equal to the inclination angle Q1 of the head profile 18b.
  • the stator blade 114 When the airflow can flow through the flow passage 15b between the stator blades 114, the stator blade 114 gradually Strengthen the guidance and adjustment of the airflow to improve the vortex of the flow channel 15b, reduce the separation loss, and then reduce the energy loss of the airflow and reduce the noise.
  • the value of Q1 ranges from 0 degrees to 30 degrees, that is, the inclination angle Q1 of the head profile 18b of each stationary blade 114 is less than or
  • the airflow is equal to 30 degrees, when the airflow enters the flow channel 15b between the stator blades 114, it can prevent the airflow angle from being adjusted too large, which may cause a large energy loss.
  • the value of Q2 ranges from 0 degrees to 40 degrees, that is, the inclination angle Q2 of the head profile 18b of each stator blade 114 is less than or equal to 40 degrees, which can avoid adjusting the air flow when the air flows through the flow passage 15b between the stator blades 114 Too large, and cause greater energy loss.
  • the value of Q1 ranges from 12 degrees to 18 degrees, so that when the airflow enters the flow channel 15b between the stator blades 114, it can be better To reduce flow separation loss and reduce noise.
  • the value range of Q2 is 20 degrees to 35 degrees, and Q2 ⁇ Q1.
  • the value of Q1 ranges from 0° to 30°, so as to prevent the airflow angle from being adjusted too large when the airflow enters the flow passage 15b between the stationary blades 114
  • the value of Q2 ranges from 15 degrees to 40 degrees to avoid excessive adjustment of the air flow when the air flows through the flow passage 15b between the stator blades 114, which may cause a large energy loss.
  • the wrap angle of each stationary blade 114 in the previous row of stationary blades 114 is greater than or equal to the wrap angle of each stationary blade 114 in the next row of stationary blades 114 angle. Setting the wrap angle of each stator blade 114 in the previous row of stator blades 114 to be larger can better guide the air flow gradually, reduce the separation loss, and improve the pressure diffusion effect.
  • the chord length La of each stationary blade 114 in the previous row of stationary blades 114 is greater than or equal to that of each stationary blade 114 in the next row of stationary blades 114 Chord length Lb; since the airflow has a relatively large circumferential velocity when entering the diffuser 10, when the airflow passes through each row of stationary blades 114, the chord length Lb of each stationary blade 114 in the previous row of stationary blades 114 is set If it is longer, it can better guide the airflow, reduce the circumferential velocity of the airflow, and be gradually guided by each row of static blades 114 to reduce separation loss.
  • the plane passing through the axial direction of the base ring 11 is the meridian surface of the diffuser 10, and the stationary blades 114 projected onto the meridian surface along the circumferential direction of the base ring 11 are the meridian surfaces.
  • the leading edge line 214 of each stationary blade 114 is a line segment where the head of the stationary blade 114 is projected onto the meridian surface.
  • the trailing edge line 215 of each stationary blade 114 is a line segment where the tail of the stationary blade 114 is projected onto the meridian surface.
  • the intersection line of the radial plane of the base ring 11 and the meridian projection plane is a line segment perpendicular to the axial direction of the base ring 11.
  • the leading edge line 214 of each stationary blade 114 is arranged obliquely to the radial surface of the base ring member 11. That is, the line segment of the leading edge line 214 of each stator blade 114 in the row of stator blades 114 on the meridian projection surface is inclined to the radial direction of the base ring 11; thus, the flow separation loss can be reduced and the diffusion effect can be improved.
  • the leading edge line 214 of each stationary blade 114 in one of the rows of stationary blades 114 may be inclined to the radial surface of the base ring 11.
  • the absolute value of the inclination angle B1 between the leading edge line 214 of each stationary blade 114 and the radial surface of the base ring member 11 is less than or equal to 25 degree.
  • the absolute value of the inclination angle B1 between the leading edge line 214 of each stator blade 114 in the second row of stator blades 13 and the radial surface of the base ring member 11 is less than or equal to 25 degrees to better reduce the flow separation loss and improve the expansion ⁇ Pressure effect.
  • the leading edge line 214 of each stationary blade 114 is inclined toward the tail of the stationary blade 114 to further control the flow separation near the blade root 17. Reduce the flow separation loss and improve the pressure diffusion effect.
  • the trailing edge line 215 of each stationary blade 114 is arranged obliquely to the radial surface of the base ring member 11. That is, the line segment of the trailing edge line 215 of each stationary blade 114 in the row of stationary blades 114 on the meridian projection surface is inclined to the radial direction of the base ring member 11; thus, the unevenness of the air flow at the outlet of the stationary blade 114 can be reduced, and the pressure diffusion can be improved. effect.
  • the trailing edge line 215 of each stationary blade 114 in one of the rows of stationary blades 114 can be arranged obliquely to the radial surface of the base ring 11.
  • the trailing edge line 215 of each of the stator blades 114 in the rows of stator blades 114 obliquely to the radial surface of the base ring 11.
  • the trailing edge line 215 of each stationary blade 114 in each row of stationary blades 114 obliquely to the radial surface of the base ring member 11.
  • the absolute value of the inclination angle B2 between the trailing edge line 215 of each stationary blade 114 and the radial surface of the base ring member 11 is less than or equal to 30 degrees.
  • the absolute value of the inclination angle B2 between the trailing edge line 215 of each stator blade 114 in the second row of stator blades 13 and the radial surface of the base ring member 11 is less than or equal to 30 degrees, so as to better improve the air flow at the exit of the stator blade 114 Uniformity, improve the effect of expansion.
  • the diffuser 10 further includes a casing (not shown), the base ring 11 is placed in the casing, and each stator blade 114 is located between the base ring 11 and the casing.
  • Setting the casing can not only protect the stator blades 114, but also can form a channel between the base ring 11 and the casing to better limit the air flow channel and ensure that the diffuser 10 can be delivered in different ways. Consistency of performance in wind installations.
  • each stationary blade 114 is in contact with the inner surface of the casing, that is, at least 80% of the tip 16 of each stationary blade 114 is in contact with the inner surface of the casing.
  • the casing, the base ring 11 and the stator blades 114 are integrally formed to ensure a good connection between the casing and the stator blades 114 and increase the strength of the diffuser 10 at the same time.
  • the casing can be made separately, and then the base ring 11 with the stator blades 114 is placed in the casing.
  • the diffuser 10 of this embodiment can not only improve the vortex flow of the flow channel 15 well, reduce the separation loss, reduce the energy loss, and improve the supercharging effect, but also can reduce the aerodynamic noise; the diffuser 10 of this embodiment can be used for air supply
  • the device can not only generate greater suction, but also has less operating noise.
  • the diffuser 10 of this embodiment can be applied not only to air supply devices, but also to electrical appliances such as dust collection equipment, range hoods, and air blowing devices.
  • this embodiment also provides an air blowing device 20, which includes a frame 221, an impeller 31, a wind cover 32, a motor 222, and the diffuser 10 as described in any of the above embodiments.
  • the diffuser 10 is installed in the frame 221, the impeller 31 is arranged at the front end of the diffuser 10, the air hood 32 is covered on the impeller 31, and the air hood 32 is installed on the frame 221, and the motor 222 is installed on the frame 221 Among them, the motor 222 is connected to the impeller 31.
  • the air blowing device 20 can reduce energy loss and operating noise by using the diffuser 10 of the above-mentioned embodiment, so that a greater suction force can be generated under the same power.
  • a bearing 225 is installed in the base ring 11, and the drive shaft 224 of the motor 222 passes through the bearing 225 and is connected to the impeller 31, so that the motor 222 drives the impeller 31 to rotate more flexibly.
  • the impeller 31 is a closed centrifugal impeller 31a.
  • the impeller 31 may also be an open centrifugal impeller.
  • the impeller 31 may also be a mixed flow impeller 31b.
  • the wind hood 32 can extend to the tail of the diffuser 10, that is, the wind hood 32 covers both the impeller 31 and the diffuser 10, so as to better reduce the airflow at the outlet of the impeller 31. Lead to diffuser 10.
  • the frame 221 may be integrally formed with the wind cover 32 to ensure the connection strength between the frame 221 and the wind cover 32.
  • the air blowing device 20 of this embodiment can be applied to electrical appliances such as dust collection equipment, range hoods, air blowing devices, fans, and the like.
  • This embodiment also discloses a dust suction device in this embodiment, which includes the air blowing device 20 as described in any of the above embodiments.
  • the dust collection equipment of this embodiment uses the above-mentioned air blowing device 20, which not only has high power, high efficiency, and low noise.
  • This embodiment is different from Embodiment 2 in that: referring to Figures 6, 9 and 10, in the multiple rows of stationary blades 114: the profile 18 of each stationary blade 114 in at least one row of stationary blades 114 faces the One side of the stationary blade 114 is inclined.
  • the profile 18 of the corresponding stationary blade 114 is inclined toward one side of the stationary blade 114, that is, the height direction of the profile 18 of the stationary blade 114 is inclined to the radial arrangement of the base ring member 11, which can effectively improve the airflow when leaving the stationary blade 114.
  • the boundary layer is separated to reduce separation loss and improve the vortex of the flow passage 15 between the stator blades 114, thereby reducing flow loss, reducing air flow energy loss, and reducing aerodynamic noise.
  • the profile 18a of each stationary blade 114 in the first row of stationary blades 12 can be arranged obliquely, so that when the airflow passes through the first row of stationary blades 12, the absolute speed of the airflow is reduced, while the separation loss is reduced, and the Boosting effect.
  • each stationary blade 114 in the second row of stationary blades 13 can be inclined so as to reduce the absolute velocity of the air flow when the air flows through the second row of stationary blades 13. , Reduce separation loss and improve booster effect.
  • the profile 18 of each of the stationary blades 114 in the first row of stationary blades 12 and each of the stationary blades 114 in the second row of stationary blades 13 can be arranged obliquely, so as to better reduce the airflow velocity and reduce the separation. Loss, reduce the unevenness of the air flow, and improve the supercharging effect.
  • the profile 18 of each stationary blade 114 in one of the rows of stationary blades 114 may be inclined.
  • the profile 18 of each of the rows of stationary blades 114 can also be inclined. It is also possible to arrange the profile 18 of each stationary blade 114 in each row of stationary blades 114 obliquely.
  • the profile 18 of the stator blade 114 is obliquely arranged toward one side of the suction surface 19 of the stator blade 114. It can better improve the separation of the airflow boundary layer, improve the vortex of the flow passage 15 between the stator blades 114, reduce energy loss, and reduce aerodynamic noise.
  • the profile 18 of the stator blade 114 is obliquely installed toward the side of the pressure surface 14 of the stator blade 114. It can better improve the unevenness of the air flow, improve the vortex of the flow passage 15 between the stator blades 114, reduce energy loss, and reduce aerodynamic noise.

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Abstract

一种扩压器(10)，包括基环件(11)和多排静叶片(114)，各排静叶片(114)沿基环件(11)轴向设于基环件(11)外环壁(111)上，并沿基环件(11)周向排布，基环件(11)的相对两侧为进风侧和出风侧，自进风侧至出风侧，其中一排静叶片(114)的弦长大于或等于与该排静叶片(114)相邻的下一排静叶片(114)的弦长；静叶片(114)具有安装角，自进风侧至出风侧，其中一排静叶片(114)的安装角小于或等于与该排静叶片(114)相邻的下一排静叶片(114)的安装角。通过在扩压器(10)上设置多排静叶片(114)，流经扩压器(10)的气流即可得到各排静叶片(114)的多级引流作用，这样便实现了气流的多级减速增压，从而降低了气流在流经扩压器(10)时产生的流动损失。

Description

扩压器、送风装置及吸尘设备
本申请要求于2020年01月06日提交国家知识产权局、申请号为202010010952.7、申请名称为“扩压器、送风装置及吸尘器”的中国专利申请的优先权；
以及，于2020年01月06日提交国家知识产权局、申请号为202010010950.8、申请名称为“扩压装置、风机及吸尘器”的中国专利申请的优先权；
以及，于2020年01月06日提交国家知识产权局、申请号为202010011558.5、申请名称为“扩压装置、风机及吸尘器”的中国专利申请的优先权；
上述三个中国专利申请的全部内容通过引用结合在本申请中。
技术领域
本申请属于清洁设备技术领域，尤其涉及一种扩压器、送风装置及吸尘设备。
 背景技术
吸尘设备内通常装设有送风装置，送风装置内设置有扩压器，以将流经送风装置的气流的动能转化为压力能，进而减少气流的流动损失。扩压器内通常设置有静叶片，以对气流进行引流和增压。
然而，现有的静叶片布局方式仍然无法充分实现气流在流经扩压器时的动能和压力能之间的转化，如此会导致气流在流经扩压器时所产生的流动损失较大。
 技术问题
本实施例的目的在于提供一种扩压器，旨在解决现有技术中的气流在流经扩压器时的流动损失较大的技术问题。
 技术解决方案
为实现上述目的，本申请采用的技术方案是：
第一方面：提供一种扩压器，包括基环件和多排静叶片，各排所述静叶片依序沿所述基环件的轴向设置于所述基环件的外环壁上，并均沿所述基环件的周向排布，所述基环件沿其轴向的相对两侧分别为进风侧和出风侧，自所述进风侧至所述出风侧，其中一排所述静叶片的弦长大于或等于与该排所述静叶片相邻的下一排所述静叶片的弦长；
所述静叶片具有安装角，自所述进风侧至所述出风侧，其中一排所述静叶片的安装角小于或等于与该排所述静叶片相邻的下一排所述静叶片的安装角。
第二方面：提供一种扩压器，包括基环件和多个静叶片，多个所述静叶片沿所述基环件的轴向依次设置呈多排，且各排静叶片中所述静叶片数量为多个，各排静叶片中多个所述静叶片沿所述基环件周向设置，所述基环件的横截面呈圆形；多排所述静叶片中至少一排静叶片中的各所述静叶片的型面朝向该静叶片的一侧倾斜设置。
第三方面：提供一种扩压器，包括基环件和多个静叶片，多个所述静叶片沿所述基环件的轴向依次设置呈多排，且各排静叶片中所述静叶片数量为多个，各排静叶片中多个所述静叶片沿所述基环件周向设置，所述基环件的横截面呈圆形；多排所述静叶片中至少一排静叶片中的各所述静叶片的厚度由该静叶片的头部至尾部呈非恒定设置。
第四方面：提供一种送风装置，包括上述的扩压器。
第五方面：提供一种吸尘设备，包括上述的送风装置。
 有益效果
本实施例至少具有如下的有益效果：本实施例提供的扩压器，通过在扩压器内，沿基环件的轴向设置多排静叶片，这样流经扩压器的气流即可得到各排静叶片的多级引流作用，这样便实现了气流的多级减速增压，从而降低了气流在流经扩压器时产生的流动损失。
本实施例提供的送风装置，由于包括有上述的扩压器，而上述的扩压器能够保证气流在流经扩压器时，能够在不发生较大流动损失的前提下，顺利地实现减速增压。如此便也提升了送风装置的整体工作效率，节省了送风装置的工作能耗。
本实施例提供的吸尘设备，由于包括有上述的送风装置，而上述的送风装置能够实现对气流较为顺畅地减速增压，且运行时节能环保，如此便也显著提升了包括有上述送风装置的吸尘设备的吸尘效果，同时也节省了吸尘设备的工作能耗。
 附图说明
为了更清楚地说明本实施例中的技术方案，下面将对实施例或现有技术描述中所需要使用的附图作简单地介绍，显而易见地，下面描述中的附图仅仅是本申请的一些实施例，对于本领域普通技术人员来讲，在不付出创造性劳动性的前提下，还可以根据这些附图获得其他的附图。
图1为本实施例提供的送风装置的结构示意图；
图2为本实施例提供的送风装置的扩压器的结构示意图；
图3为本实施例提供的送风装置的扩压器的第一排静叶片的叶栅图；
图4为本实施例提供的送风装置的扩压器的第一排静叶片和第二排静叶片的叶栅图；
图5为本实施例提供的送风装置的扩压器的基环件的结构示意图；
图6为本申请实施例提供的扩压器的立体结构示意图；
图7为图6的扩压器的叶栅平面示意图；
图8为图6的扩压器的正视结构示意图；
图9为图8的扩压器中基环件及第二排静叶片的俯视结构示意图；
图10为图8的扩压器中基环件及第二排静叶片的仰视结构示意图；
图11为沿图8中A-A线的剖面结构示意图；
图12为本申请实施例提供的扩压器中基环件及一排静叶片沿基环件径向面的剖视结构示意图；
图13为本申请实施例提供的扩压器中一个静叶片于子午投影面的示意图；
图14为本申请实施例提供的扩压器沿穿过基环件轴线的剖视结构示意图；
图15为本申请实施例提供的第一种送风装置的剖视结构示意图；
图16为本申请实施例提供的第二种送风装置的剖视结构示意图。
其中，图中各附图标记：
10—扩压器              11—基环件            12—第一排静叶片
13—第二排静叶片14—压力面15—流道
16—叶尖17—叶根              18—型面
19—吸力面              20—送风装置          21—风罩
22—驱动机构23—动叶轮            24—进风口
111—外环壁             112—内环壁113—安装孔
114—静叶片221—机架             222—马达
223—电路基板224—驱动轴             225—轴承。
 本发明的实施方式
下面详细描述本申请的实施例，所述实施例的示例在附图中示出，其中自始至终相同或类似的标号表示相同或类似的元件或具有相同或类似功能的元件。下面通过参考附图1~16描述的实施例是示例性的，旨在用于解释本申请，而不能理解为对本申请的限制。
在本申请的描述中，需要理解的是，术语“长度”、“宽度”、“上”、“下”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”“内”、“外”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本申请和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本申请的限制。
此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括一个或者更多个该特征。在本申请的描述中，“多个”的含义是两个或两个以上，除非另有明确具体的限定。
在本申请中，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”、“固定”等术语应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或成一体；可以是机械连接，也可以是电连接；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通或两个元件的相互作用关系。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本申请中的具体含义。
实施例1
如图1、图2和图4所示，本实施例提供了一种扩压器10，用于送风装置20，该送风装置20可以但不限于用于吸尘设备。其中，如图5所示，扩压器10包括基环件11和若干排静叶片114，各排静叶片114依序沿基环件11的轴向设置于基环件11的外环壁111上，并均沿基环件11的周向排布，基环件11沿其轴向的相对两侧分别为进风侧和出风侧，且基环件11具有外环壁111和内环壁112，内环壁112内开设有若干安装孔113，基环件11通过锁紧螺栓穿设安装孔113和机架221以实现在扩压器10内的固定连接。自进风侧至出风侧，其中一排静叶片114的弦长大于或等于与该排静叶片114相邻的下一排静叶片114的弦长。静叶片114具有安装角，自进风侧至出风侧，其中一排静叶片114的安装角小于或等于与该排静叶片114相邻的下一排静叶片114的安装角。
首先，结合图3对本实施例中涉及的技术术语进行解释说明：
前额线，多个同一排的静叶片114的头部对应点的连接线称为前额线（图3中L1所示）；
后额线，多个同一排的静叶片114的尾部对应点的连接线称为后额线（图3中L2所示）；
入口安放角：中线与前额线在叶片头部的切线所形成的夹角（图3中α所示）；
出口安放角：中线与后额线在叶片尾部的切线所形成的夹角（图3中β所示）；
安装角：是指静叶片114的前额线与弦长之间的夹角，该角度随着弦长的变化而变化，（图3中θ所示）；
静叶片114的头部：沿基环件11的轴向，静叶片114的最前位置为头部（图3中a所示）；
静叶片114的尾部：沿基环件11的轴向，静叶片114的最后位置为尾部（图3中b所示）；
静叶片114的高度：静叶片114沿基环件11的径向方向的长度；
叶顶：静叶片114沿其径向增加到顶部的位置为叶顶；
弦长：中线在静叶片114的头部和静叶片114的尾部之间的直线距离为弦长（图3中L4所示）；
中线：静叶片114的厚度方向的各中点从静叶片114的头部至尾部连线而成的曲线称为中线（图3中L3所示）。
本实施例提供的扩压器，通过在扩压器内，沿基环件的轴向设置多排静叶片114，这样流经扩压器的气流即可得到各排静叶片114的多级引流作用，这样便实现了气流的多级减速增压，从而降低了气流在流经扩压器时产生的流动损失。
以下对本实施例提供的扩压器10作更进一步说明：本实施例提供的扩压器10，通过在扩压器10内，沿基环件11的轴向设置多排静叶片114，这样流经扩压器10的气流即可得到各排静叶片114的多级引流作用，这样便首先实现了气流的多级减速增压。而通过使得自基环件11的进风侧至出风侧，其中一排静叶片114的弦长大于或等于与该排静叶片114相邻的下一排静叶片114的弦长。这样便使得各排静叶片114能够逐级减弱气流产生的流动分离现象，显著降低了气流在流经扩压器10时产生的流动损失。如此便使得气流能够在各排静叶片114的引流作用下，在不发生较大流动损失的前提下，顺利地实现减速增压。
在本实施例中，静叶片114的头部具有入口安放角，自进风侧至出风侧，其中一排静叶片114的入口安放角小于或等于与该排静叶片114相邻的下一排静叶片114的入口安放角。其中一排静叶片114的出口安放角小于或等于与该排静叶片114相邻的下一排静叶片114的出口安放角。
具体地，通过使得其中一排静叶片114的入口安放角小于或等于下一排静叶片114的入口安放角，其中一排静叶片114的出口安放角小于或等于下一排静叶片114的出口安放角，这样便进一步有效抑制了气流自上一排静叶片114流动至下一排静叶片114时的流动不均匀性，同时也有效抑制了气流自上一排静叶片114流动至下一排静叶片114时产生的流动分离现象，进而有效降低了气流自上一排静叶片114流动至下一排静叶片114时所产生的流动损失，提升了气流流动效率。
在本实施例中，静叶片114的尾部具有出口安放角，自进风侧至出风侧，其中一排静叶片114的出口安放角可以小于或等于与该排静叶片114相邻的下一排静叶片114的入口安放角。使得气流自上一排静叶片114流畅地流动至下一排静叶片114。在本实施例中，其中一排静叶片114的出口安放角也可以大于与该排相邻的下一排静叶片114的入口安放角。
在本实施例中，如图2所示，扩压器10包括第一排静叶片12和第二排静叶片13，第一排静叶片12和第二排静叶片13自进风侧至出风侧依序沿基环件11的轴向设置于基环件11的外环壁111上。具体地，静叶片114的排数可以为两排，这样一方面保证了具有足够数量的静叶片114对气流进行充分的引流和扩压，另一方面也保证了静叶片114的排数不会过多，进而实现了扩压器10的紧凑性设计。
在本实施例中，第一排静叶片12的入口安放角的角度值为5°~20°，第二排静叶片13的入口安放角的角度值为20°~40°。具体地，第一排静叶片12的入口安放角的角度值可为5°、5.5°、6°、6.5°、7°、7.5°、8°、8.5°、9°、9.5°、10°、10.5°、11°、11.5°、12°、12.5°、13°、13.5°、14°、14.5°、15°、15.5°、16°、16.5°、17°、17.5°、18°、18.5°、19°、19.5或20°。
第二排静叶片13的入口安放角的角度值可为20°、20.5°、21°、21.5°、22°、22.5°、23°、23.5°、24°、24.5°、25°、25.5°、26°、26.5°、27°、27.5°、28°、28.5°、29°、29.5°、30°、30.5°、31°、31.5°、32°、32.5°、33°、33.5°、34°、34.5、35°、35.5°、36°、36.5°、37°、37.5°、38°、38.5°、39°、39.5°或40°。
通过将第一排静叶片12的入口安放角的角度值设定为5°~20°，并将第二排静叶片13的入口安放角的角度值设定为20°~40°，这样便进一步实现了对气流流经第一排静叶片12和第二排静叶片13时产生的流动不均匀性的有效抑制，同时也保证了第二排静叶片13对气流的有效引流。
在本实施例中，第一排静叶片12的出口安放角的角度值为10°~60°，第二排静叶片13的入口安放角的角度值为60°~80°。具体地，第一排静叶片12的出口安放角的角度值可为10°、15°、20°、25°、30°、35°、40°、45°、50°、55°或60°。第二排静叶片13的入口安放角的角度值可为60°、61°、62°、63°、64°、65°、66°、67°、68°、69°、70°、71°、72°、73°、74°、75°、76°、77°、78°、79°或80°。
通过将第一排静叶片12的出口安放角的角度值设定为10°~60°，第二排静叶片13的入口安放角的角度值设定为60°~80°，这样便有效减弱了气流自第一排静叶片12流动至第二排静叶片13时产生的流动分离现象，进而优化了气流的流动状态，进一步降低了气流自第一排静叶片12流动至第二排静叶片13时所产生的流动损失，同时也进一步提升了气流流动效率。
在本实施例中，第一排静叶片12的弦长和第二排静叶片13的弦长之比大于等于1，且小于等于5。具体地，通过使得第一排静叶片12的弦长和第二排静叶片13的弦长之比可以为1、1.2、1.5、1.7、2、2.2、2.5、2.7、3、3、3.2、3.5、3.7、4、4.2、4.5、4.7或5。通过使得第一排静叶片12的弦长和第二排静叶片13的弦长之比大于等于1，且小于等于5。如此便进一步减弱了气流自第一排静叶片12至第二排静叶片13时所产生的流动分离现象，进一步降低了气流在流经扩压器10时产生的流动损失。
在本实施例中，第一排静叶片12的叶片数小于或等于第二排静叶片13的叶片数，第一排静叶片12和第二排静叶片13各自延外环壁的周向均匀分布，第一排静叶片12和第二排静叶片13于外环壁的轴向相互错位分布，至少第一排静叶片12中的一个静叶片114的头部或尾部与第二排静叶片13中的一个静叶片114的头部或尾部于外环壁的轴向对齐。如此可使得第一排静叶片12和第二排静叶片13的衔接性更强，从而有利于气流自第一排静叶片12至第二排静叶片13的高效流动。
在本实施例中，第一排静叶片12的叶片数为6片~20片，第二排静叶片13的叶片数为10片~30片。具体地，第一排静叶片12的叶片数可以为6片、7片、8片、9片、10片、11片、12片、13片、14片、15片、16片、17片、18片、19片或20片，第二排静叶片13的叶片数可以为10片、11片、12片、13片、14片、15片、16片、17片、18片、19片、20片、21片、22片、23片、24片、25片、26片、27片、28片、29片或30片。通过将第一排静叶片12的叶片数设定为6片~20片，且将第二排静叶片13的叶片数设定为10片~30片。这样气流在自第一排静叶片12流动至第二排静叶片13时，即可受到第二排静叶片13更为充分地引流和扩压作用，而进一步减小流速，增大压力，如此便进一步提升了扩压器10的增压效果。
在本实施例中，第一排静叶片12和第二排静叶片13并不一一对应，亦并非是严格的N对一关系，而是先确定第二排静叶片13的数量后，先定位第二排静叶片13中的某一个静叶片114和第一排静叶片12中的某一个静叶片114的某一端对齐，然后再将第二排静叶片13均布于基环件11的外环壁上，完成对第二排静叶片13的布局后，再进行第一排静叶片12的布局。
在本实施例中，如图4所示，第一排静叶片12的头部和第二排静叶片13的尾部之间的沿基环件11轴向的间距（图4中D所示）小于等于3mm。具体地，通过使得第一排静叶片12的头部和第二排静叶片13的尾部之间的沿基环件11轴向的间距小于等于3mm，这样一方面保证了第一排静叶片12和第二排静叶片13对气流引流的顺畅衔接，保证了气流的流动效率，另一方面也为第一排静叶片12和第二排静叶片13留出了足够的装配间隙，避免因为第一排静叶片12和第二排静叶片13的加工尺寸误差而导致第一排静叶片12和第二排静叶片13相互干涉。
可选地，第一排静叶片12的头部和第二排静叶片13的尾部之间的沿基环件11轴向的间距大于等于1mm，且小于等于3mm。通过将第一排静叶片12的头部和第二排静叶片13的尾部之间的沿基环件11轴向的间距进一步限定为大于等于1mm，且小于等于3mm，如此便在保证气流的流动效率和避免第一排静叶片12和第二排静叶片13相互干涉之间求得了最佳平衡，使得第一排静叶片12和第二排静叶片13在避免相互干涉的前提下，能够对流经第一排静叶片12和第二排静叶片13的气流实现最优的引流和扩压效果。
在本实施例中，出口安放角包括位于静叶片114的叶根处的第一出口安放角和位于静叶片114的叶顶处的第二出口安放角，第一出口安放角的角度值和第二出口安放角的角度值的差值为0°~20°。
如此，当第一出口安放角的角度值和第二出口安放角的角度值的差值不为0°时，静叶片114沿基环件11径向方向的轮廓型线即为曲线，说明静叶片114沿基环件11径向方向进行了弯曲。当两者的角度值的差值为0°时，说明静叶片114沿基环件11径向方向平直延伸，出口安放角的角度值沿径向方向不变。
具体地，第一出口安放角的角度值和第二出口安放角的角度值的差值可以为0°、1°、2°、3°、4°、5°、6°、7°、8°、9°、10°、11°、12°、13°、14°、15°、16°、17°、18°、19°或20°。
通过将静叶片114靠近基环件11的外环壁111的出口安放角的角度值和静叶片114靠近其叶顶端面的出口安放角的角度值的差值设定为0°~20°，如此便进一步地抑制了气流在静叶片114尾部的流动的不均匀性，从而也进一步保证了静叶片114对气流的有效引流。
在本实施例中，如图2所示，静叶片114为弧形叶片。具体地，通过将静叶片114设定为弧形叶片，这样便使得静叶片114具有了更为顺畅和平滑的引流曲线，进而保证了气流能够更为顺畅且稳定地流过静叶片114。
在本实施例中，如图1所示，扩压器10的各静叶片114的顶端面均和风罩21的内侧壁相抵接。具体地，通过使得各静叶片114的顶端面均和风罩21的内侧壁相抵接，这样可使得各静叶片114能够充分占据基环件11和风罩21之间所围成的区域，进而实现对进入送风装置20的气流实现充分的引流作用，进而实现对气流进行充分的扩压减速。
基于上述参数设置，提供几种具体的扩压器10结构，在本实施例中，第一排静叶片12的入口安放角为15°，出口安放角为24°，第二排静叶片13的入口安放角为35°，出口安放角为75°。且第一排静叶片12的尾部和对应的第二排静叶片13的头部之间的轴向距离为1.8mm，当扩压器10按照上述参数取值时，具有良好的气动性能，按IEC60312标准，在13mm孔板测量条件下具有上述扩压器的送风装置20的整机效率在54%左右。
在本实施例中，第一排静叶片12的入口安放角为20°，出口安放角为27°，第二排静叶片13的入口安放角为42°，出口安放角为60°。且第一排静叶片12的尾部和对应的第二排静叶片13的头部之间的轴向距离为1.3mm，当扩压器10按照上述参数取值时，具有良好的气动性能，按IEC60312标准，在13mm孔板测量条件下具有上述扩压器10的送风装置20的整机效率在54.2%左右。
本实施例还提供了一种送风装置20，其包括有上述的扩压器10。具体地，送风装置20包括风罩21、驱动机构22、动叶轮23和扩压器10，驱动机构22设置于风罩21内，动叶轮23和驱动机构22相连接，并对应风罩21的进风口24设置，扩压器10固定于风罩21内，并位于动叶轮23背离进风口24的一侧。
具体地，驱动机构22包括机架221、马达222和电路基板223，机架221和电路基板223均固定于风罩21内，马达222设置于机架221上，且马达222的驱动轴224穿过机架221和扩压器10并和动叶轮23相连接，以驱动动叶轮23转动。
本实施例提供的送风装置，由于包括有上述的扩压器，而上述的扩压器能够保证气流在流经扩压器时，能够在不发生较大流动损失的前提下，顺利地实现减速增压。如此便也提升了送风装置的整体工作效率，节省了送风装置的工作能耗。
本实施例还提供了一种吸尘设备，包括有上述的送风装置。本实施例提供的吸尘设备，由于包括有上述的送风装置，而上述的送风装置能够实现对气流较为顺畅地减速增压，且运行时节能环保，如此便也显著提升了包括有上述送风装置的吸尘设备的吸尘效果，同时也节省了吸尘设备的工作能耗。
实施例2
请参阅图6和图7，现对本实施例提供的扩压器10进行说明：扩压器10包括基环件11和多个静叶片114，多个静叶片114分成多排设置，多排静叶片114沿基环件11的轴向设置，每排静叶片114中静叶片114数量为多个，每排静叶片114中的多个静叶片114沿基环件11周向设置；从而相邻两个静叶片114之间可以形成导引气流流动的流道15。气流经基环件11周侧的相邻两个静叶片114之间流道15时，会被静叶片114引导流动，而使气流流动更为平稳，减小涡流，降低能量损失。基环件11的横截面呈圆形，使气流由偏向基环件11径向转动沿基环件11轴向流动时，流动到基环件11周侧各处距离相近，使其受到阻力也相近，从而使气流更平稳流动到基环件11周侧，降低能量损失。而将多个静叶片114沿基环件11轴向设置呈多排，可以通过多排静叶片114逐步引导气流流动，降低能量损失，提升扩压效果。
为方便描述，定义：气流流过该扩压器10时，气流入口的方向为上、前或头，气流出口的方向为下、后或尾。
为方便描述，定义：多个静叶片114沿基环件11的轴向分成两排，由上至下依次为第一排静叶片12和第二排静叶片13，即第一排静叶片12为第二排静叶片13的上一排，第二排静叶片13为第一排静叶片12的下一排。多个静叶片114沿基环件11的轴向分成三排，由上至下依次为第一排静叶片12、第二排静叶片13和第三排静叶片114。多个静叶片114沿基环件11的轴向分成四排或更多排，则由上至下依次为第一排静叶片12、第二排静叶片13、第三排静叶片114……。即多个静叶片114沿基环件11轴向设置呈N（N为正整数，N≥2）排时，由上到下依次分为第一排、第二排……第N排；其中，第M-1排静叶片114为第M排静叶片114的上一排静叶片114，第M排静叶片114为第M-1排静叶片114的下一排静叶片114，（M为正整数，M≤N）。
请一并参阅图11，静叶片114的型面18指该静叶片114叶根17与叶尖16之间的两个侧面；静叶片114叶根17与叶尖16之间的两个侧面分别为吸力面19与压力面14，吸力面19与压力面14统称为型面18；而静叶片114的叶根17指静叶片114高度上靠近基环件11的根部位置；静叶片114的叶尖16指静叶片114高度上远离基环件11的顶部位置；静叶片114的头部指沿气流流动方向位于静叶片114前端的部位，即静叶片114上开始接触气流的部位；静叶片114的尾部指沿气流流动方向位于静叶片114后端的部位，即气流离开静叶片114时对应的静叶片114上的部位。
请参阅图6，第一排静叶片12中：各静叶片114的两个侧面分别为吸力面19a与压力面14a，吸力面19a与压力面14a统称为该静叶片114的型面18a；相邻两个静叶片114之间可以形成导引气流流动的流道15a。第二排静叶片13中：各静叶片114的两个侧面分别为吸力面19b与压力面14b，吸力面19b与压力面14b统称为该静叶片114的型面18b；相邻两个静叶片114之间可以形成导引气流流动的流道15b。
在本实施例中，请参阅图6，多个静叶片114沿基环件11的轴向分成两排，由上至下依次为第一排静叶片12和第二排静叶片13，即第一排静叶片12为第二排静叶片13的上一排，第二排静叶片13为第一排静叶片12的下一排。在一些实施例中，多个静叶片114沿基环件11的轴向分成三排、四排或更多排。
在本实施例中，请参阅图7，在静叶片114高度方向中部截取一个等单位厚度的与基环件11形状相同的曲面，该曲面呈圆筒状，该曲面与基环件11同轴，将该曲面进行平面展开，得到各静叶片114的平面叶栅图。平面叶栅图上，各排静叶片114中各静叶片114头部对应点的连接线称为该排静叶片114的前额线L1，同时前额线L1为该排静叶片114中各静叶片114头部对应点的切线；各排静叶片114中各静叶片114尾部对应点的连接线称为该排静叶片114的后额线L2，同时后额线L2为该排静叶片114中各静叶片114尾部对应点的切线；各静叶片114厚度H中点所连成的曲线称为该静叶片114的中线L3；中线L3在相应静叶片114头部的切线与该静叶片114头部对应点切线的夹角为入口安放角α，即中线L3在静叶片114头部的切线与对应前额线L1的夹角为入口安放角α；中线L3在静叶片114尾部的切线与该静叶片114尾部对应点切线的夹角为出口安放角β，即中线L3在静叶片114尾部的切线与相应后额线L2的夹角为出口安放角β；中线L3在静叶片114的头部到尾部之间的距离为弦长L4，中线L3上不同位置到静叶片114头部之间的直线距离为位置弦长L5，即中线L3上各点到静叶片114头部之间的直线距离为该点的位置弦长L5；静叶片114某位置的位置弦长L5具有安装角θ，位置弦长L5的安装角θ为该位置与该静叶片114头部同高度处之间线段与相应前额线L1的夹角。
以第一排静叶片12为例：第一排静叶片12中各静叶片114头部对应点的连接线为第一排静叶片12的前额线L1a，同时该前额线L1a为第一排静叶片12中各静叶片114头部对应点的切线；第一排静叶片12中各静叶片114尾部对应点的连接线为第一排静叶片12的后额线L2a，同时该后额线L2a为第一排静叶片12中各静叶片114尾部对应点的切线；第一排静叶片12中各静叶片114厚度Ha中点所连成的曲线称为该静叶片114的中线L3a；第一排静叶片12中各静叶片114的中线L3a在该静叶片114头部的切线与该静叶片114头部对应点切线的夹角为入口安放角αa；第一排静叶片12中各静叶片114的中线L3a在该静叶片114尾部的切线与该静叶片114尾部对应点切线的夹角为出口安放角βa；第一排静叶片12中各静叶片114的中线L3a在该静叶片114的头部到尾部之间的距离为该静叶片114的弦长La，第一排静叶片12中各静叶片114的中线L3a上某点到该静叶片114头部之间的直线距离为该静叶片114上相应点的位置弦长L5a；第一排静叶片12中各静叶片114某位置的位置弦长L5a具有安装角θa，位置弦长L5a的安装角θa为该位置与该静叶片114头部同高度处之间线段与相应前额线L1a的夹角。
以第二排静叶片13为例：第二排静叶片13中各静叶片114头部对应点的连接线为第二排静叶片13的前额线L1b，同时该前额线L1b为第二排静叶片13中各静叶片114头部对应点的切线；第二排静叶片13中各静叶片114尾部对应点的连接线为第二排静叶片13的后额线L2b，同时该后额线L2b为第二排静叶片13中各静叶片114尾部对应点的切线；第二排静叶片13中各静叶片114厚度Hb中点所连成的曲线称为该静叶片114的中线L3b；第二排静叶片13中各静叶片114的中线L3b在该静叶片114头部的切线与该静叶片114头部对应点切线的夹角为入口安放角αb；第二排静叶片13中各静叶片114的中线L3b在该静叶片114尾部的切线与该静叶片114尾部对应点切线的夹角为出口安放角βb；第二排静叶片13中各静叶片114的中线L3b在该静叶片114的头部到尾部之间的距离为该静叶片114的弦长Lb，第二排静叶片13中各静叶片114的中线L3b上某点到该静叶片114头部之间的直线距离为该静叶片114上相应点的位置弦长L5b；第二排静叶片13中各静叶片114某位置的位置弦长L5b具有安装角θb，位置弦长L5b的安装角θb为该位置与该静叶片114头部同高度处之间线段与相应前额线L1b的夹角。
在本实施例中，请参阅图6和图7，多排静叶片114中：至少一排静叶片114中的各静叶片114的厚度H由该静叶片114的头部至尾部呈非恒定设置，从而在气流进入该排静叶片114中相邻两静叶片114间流道15时，改善流动分离，减小流动分离损失；而在气流流经该排静叶片114中静叶片114间流道15时可以改善涡流，调控叶根17处流动分离；而气流流出该排静叶片114中静叶片114间流道15时，可以减小气流不均匀性，提升扩压效果，降低气动噪音。
本实施例的扩压器10，通过在基环件11的周向设置多排静叶片114，通过多排静叶片114逐步引导气流，降低气流的绝对速度，以提升增压效果；并至少一排静叶片114中各静叶片114的厚度H由该静叶片114的头部至尾部呈非恒定设置，则气流进入该排静叶片114中相邻两静叶片114间流道15时，可以改善流动分离，减小流动分离损失；而在气流流经该排静叶片114中静叶片114间流道15时，可以改善涡流，调控叶根17处流动分离；而气流流出该排静叶片114中静叶片114间流道15时，可以减小气流不均匀性，提升扩压效果，降低气动噪音。
在本实施例中，各静叶片114的长度方向倾斜于基环件11的轴向，各静叶片114的长度方向指该静叶片114头部与尾部连接的方向，则气流在流经两静叶片114之间流道15时，可以逐渐引导气流变向，减小气流能量损失。
在本实施例中，当扩压器10包括多排静叶片114时，可以将其中一排静叶片114中各静叶片114的厚度H由该静叶片114的头部至尾部呈非恒定设置。当然也可以将其中几排静叶片114中各静叶片114的厚度H由该静叶片114的头部至尾部呈非恒定设置。还可以将各排静叶片114中各静叶片114的厚度H由该静叶片114的头部至尾部均呈非恒定设置。
在本实施例中，对于厚度H非恒定设置的各静叶片114中：各静叶片114的厚度H由该静叶片114的头部至尾部呈先逐渐增大再逐渐减小，以便气流经静叶片114间流道15时，先逐步降低气流的周向速度和绝对速度，降低流动分离损失；然后改善涡流，降低气流流出静叶片114间流道15的不均匀性，降低流动分离损失，提升扩压效果，减小气动噪音。
在本实施例中，请参阅图6和图7，对于厚度H非恒定设置的各静叶片114中：各静叶片114厚度H最大处的位置弦长L5为该静叶片114弦长L的30%~45%，即各静叶片114中线上各点对应的厚度H中，厚度H最大处对应中线上的点的位置弦长L5为该静叶片114弦长L的30%~45%；以便气流在静叶片114先降低气流的周向速度和绝对速度后，逐步引导气流，提升气流的流动均匀性，降低流动分离损失，提升扩压效果，减小气动噪音。
以第一排静叶片12为例：当第一排静叶片12中各静叶片114的厚度Ha非恒定设置时，该排静叶片114中各静叶片114中线上各位置对应厚度Ha中，厚度Ha最大处对应的点的位置弦长L5a为该静叶片114弦长La的30%~45%。
以第二排静叶片13为例：当第二排静叶片13中各静叶片114的厚度Hb非恒定设置时，该排静叶片114中各静叶片114中线上各位置对应厚度Hb中，厚度Hb最大处对应的点的位置弦长L5b为该静叶片114弦长Lb的30%~45%。
在本实施例中，请参阅图6和图7，对于厚度H非恒定设置的各静叶片114中：各静叶片114厚度H最大处的位置弦长L5为该静叶片114弦长L的35%~40%，即各静叶片114中线上各点对应的厚度H中，厚度H最大处对应中线上的点的位置弦长L5为该静叶片114弦长L的35%~40%；以降低流动分离损失，改善涡流，提升扩压效果，减小气动噪音。
在本实施例中，请参阅图6和图7，第二排静叶片13中：各静叶片114厚度Hb满足如下关系，即第二排静叶片13中：各静叶片114中线上各点对应的厚度Hb满足如下关系：
各静叶片114头部的厚度范围为0.1-0.8mm；
各静叶片114位置弦长L5b为该静叶片114弦长Lb的40%处的厚度Hb范围为1.1-1.4mm；
各静叶片114尾部的厚度范围为0.1-1mm。
以更好的降低流动分离损失，改善涡流，提升扩压效果，减小气动噪音。
在本实施例中，请参阅图6和图7，第二排静叶片13中：各静叶片114厚度Hb满足如下关系，即第二排静叶片13中：各静叶片114中线上各点对应的厚度Hb满足如下关系：
各静叶片114头部的厚度范围为0.1-0.8mm；
各静叶片114位置弦长L5b为该静叶片114弦长Lb的30%处的厚度Hb范围为1-1.3mm；
各静叶片114位置弦长L5b为该静叶片114弦长Lb的40%处的厚度Hb范围为1.1-1.4mm；
各静叶片114位置弦长L5b为该静叶片114弦长Lb的50%处的厚度Hb范围为1-1.3mm；
各静叶片114位置弦长L5b为该静叶片114弦长Lb的60%处的厚度Hb范围为0.9-1.2mm；
各静叶片114位置弦长L5b为该静叶片114弦长Lb的70%处的厚度Hb范围为0.8-1.1mm；
各静叶片114尾部的厚度范围为0.1-1mm。
以更好的确定静叶片114各处厚度，进而降低流动分离损失，改善涡流，提升扩压效果，减小气动噪音。
在本实施例中，请参阅图6和图7，第二排静叶片13中：各所述静叶片114中线上各点对应厚度Hb满足如下公式：
T2≤Hb≤T1；
T1=0.82+0.68L1b-0.17L1b 2+0.011L1b 3；
T2=0.68L1b-0.17L1b 2+0.011L1b 3；
其中，L1b为所述静叶片114中线上对应点到该静叶片114头部的距离，即L1b为静叶片114中线上对应点的位置弦长，L1b 2为L1b的平方，L1b 3为L1b的3次方，0.68L1b为0.68乘以L1b，0.17L1b 2为0.17乘以L1b 2，0.011L1b 3为0.011乘以L1b 3，T1为所述静叶片114中线上对应点处的最大厚度关系式，T2为所述静叶片114中线上对应点处的最小厚度关系式。
通过上述公式确定第二排静叶片13中各静叶片114中线上各点对应厚度Hb，可以更好的降低流动损失，改善气流的不均匀性，改善涡流，提升扩压效果，减小气动噪音。
在本实施例中，请参阅图7，各所述静叶片114中线上各点对应厚度Hb满足如下公式：Hb=0.32+0.68L1b-0.17L1b 2+0.011L1b 3；其中，L1b为所述静叶片114中线上对应点到该静叶片114头部的距离，即L1b为静叶片114中线上对应点的位置弦长，L1b 2为L1b的平方，L1b 3为L1b的3次方，0.68L1b为0.68乘以L1b，0.17L1b 2为0.17乘以L1b 2，0.011L1b 3为0.011乘以L1b 3。以更好的确定第二排静叶片13中各静叶片114的厚度，更好的降低流动损失，改善气流的不均匀性，改善涡流，提升扩压效果，减小气动噪音。
在本实施例中，请一并参阅图6和图8，基环件11的外径范围为35-80mm。从而使静叶片114的厚度H与基环件11更好的匹配，保证相邻静叶片114间流道15的大小，减小对气流的阻力，减小能量损失，提升扩压效果。
在本实施例中，请参阅图12，对于厚度H非恒定设置的各静叶片114中：各静叶片114中线上任意位置对应叶根17厚度为H1，该位置叶尖16处厚度为H2，H1≥H2，即各静叶片114中线上任意位置叶根17厚度H1大于或等于该位置叶尖16处厚度H2，以更好的调控叶根17附近的流动分离，减小流动分离损失，提升扩压效果。
在本实施例中，请参阅图12，对于厚度H非恒定设置的各静叶片114中：0≤H1-H2≤0.5mm；即各静叶片114任意位置叶根17比叶尖16厚小于或等于0.5mm，从而方便加工制作，并且保证各静叶片114各位置叶尖16的强度，同时调控叶根17附近的流动分离，减小流动分离损失，提升扩压效果。
在本实施例中，请参阅图12，对于厚度H非恒定设置的各静叶片114中：各静叶片114中线上各处的厚度H由该静叶片114的叶根17至叶尖16呈逐渐增大设置，以更好的调控叶根17附近的流动分离，减小流动分离损失，提升扩压效果。
由于扩压器10在使用时，气流由动叶轮出口偏径向且高速周向流动，并在风罩极短的距离转为轴向进入扩压器10，因而动叶轮出口流动分离较严重。
在本实施例中，各静叶片114各处的安装角θ由该静叶片114的头部至尾部呈逐渐增大设置，以逐步降低气流的周向速度和绝对速度，提升减速增压效果，同时配合静叶片114型面18倾斜，可以进一步降低流道15涡流，降低能量损失，提升增压效果。
在本实施例中，静叶片114不同位置弦长L5的安装角θ变化为：静叶片114前半段各处的安装角θ基本与入口安放角α相等，使得前半段静叶片114间流道15面积均匀增加，达到均匀降低气流绝对速度和增压效果。静叶片114后半段安装角θ由入口安放角α增加到出口安放角β，以降低气流的周向速度和绝对速度，进一步提高减速增压效果。
在本实施例中，请参阅图7，第一排静叶片12中：各静叶片114的入口安放角αa的范围为5度~10度。将各静叶片114的入口安放角αa的范围为5度~10度，可以更好的匹配静叶片114入口的具有高周向速度的气流，以均匀降低气流绝对速度，提升增压效果。
在本实施例中，请参阅图7，第二排静叶片13中：各静叶片114的入口安放角αb的范围为20度~60度。将各静叶片114的入口安放角αb的范围为20度~60度，可以更好的匹配静叶片114入口的具有高周向速度的气流，以均匀降低气流绝对速度，提升增压效果。
在本实施例中，第一排静叶片12中：各静叶片114的入口安放角αa的范围为5度~10度。第二排静叶片13中：各静叶片114的入口安放角αb的范围为20度~60度。可以使气流经第一排静叶片12到第二排静叶片13，可以逐渐减小周向速度和绝对速度，减小第一排静叶片12尾部的气流的不均匀性，进而减小流动损失，提升增压效果。
在本实施例中，第一排静叶片12中：各静叶片114的出口安放角βa的范围为10度~20度，由于气流从静叶片114尾部流出时，气流角度分布更为不均匀，将出口安放角βa的范围为10度~20度，可以进一步抑制静叶片114尾部出口流动的不均匀性，以降低能量损失，提升减速增压效果。
在本实施例中，第一排静叶片12中：各静叶片114的入口安放角αa的范围为10度~20度。第二排静叶片13中：各静叶片114的入口安放角αb的范围为20度~60度。可以使气流经第一排静叶片12到第二排静叶片13，可以逐渐减小周向速度和绝对速度，在气流流动过程中平缓减小流动损失，提升增压效果。
在本实施例中，第二排静叶片13中：各静叶片114的出口安放角βb的范围为50度~90度，由于气流从静叶片114尾部流出时，气流角度分布更为不均匀，将出口安放角βb的范围为50度~90度，可以进一步抑制静叶片114尾部出口流动的不均匀性，以降低能量损失，提升减速增压效果。
在本实施例中，第一排静叶片12中：各静叶片114的入口安放角αa的范围为10度~20度。第二排静叶片13中：各静叶片114的入口安放角αb的范围为50度~90度。可以使气流经第一排静叶片12到第二排静叶片13，可以逐渐减小周向速度和绝对速度，减小第一排静叶片12尾部的气流的不均匀性，提升增压效果。
在本实施例中，第二排静叶片13中：各静叶片114的出口安放角βb的范围为60度~90度，且各静叶片114的入口安放角ka的范围为25度~50度，以更好的抑制静叶片114尾部出口流动的不均匀性，以降低能量损失，提升减速增压效果。
在本实施例中，各静叶片114的入口安放角α沿基环件11的径向变化幅度小于或等于10度，即各静叶片114的入口安放角α由叶根17到叶尖16变化幅度小于或等于10度，且各静叶片114叶根17处的入口安放角α大于或等于该静叶片114叶尖16处的入口安放角α，一方面可以方便加工制作，另一方面可以降低流动分离损失，提升扩压效果。
在本实施例中，请参阅图6和图8，相邻两排静叶片114中：下一排静叶片114中静叶片114的数量为上一排静叶片114中静叶片114数量的1.5~3倍。将上一排静叶片114中静叶片114的数量相对较少，而下一排静叶片114中静叶片114数量设置较多，从而在气流依次经过各排静叶片114时，可以逐步加强引导气流，对气流减速，提升增压效果。
在本实施例中，请参阅图6和图8，相邻两排静叶片114中：上一排静叶片114中各静叶片114的尾部沿基环件11的周向偏离邻近的下一排相应静叶片114的头部角度小于或等于20度。即穿过上一排静叶片114中各静叶片114的尾部之叶根17与基环件11轴线的平面，穿过下一排相应静叶片114的头部之叶根17与基环件11轴线的平面，该两个平面之间的夹角小于或等于20度，以减小气流流动的不均匀性，减小流动分离损失，提升增压效果。
在本实施例中，请参阅图14，相邻两排静叶片114中：上一排静叶片114中各静叶片114的尾部与邻近的下一排相应所述静叶片114的头部对齐设置，以减小气流流动的不均匀性，减小流动分离损失，提升增压效果。
在本实施例中，请参阅图9、图10和图11，静叶片114上某点处的型面18倾斜角Q是指：穿过静叶片114上该点的基环件11之径向面，静叶片114的型面18与该径向面相交的线段与穿过静叶片114上该点的径向线的夹角。
本实施例中基环件11的径向面指垂直于基环件11轴向的平面，径向线为基环件11的径向线，基环件11的径向线指沿基环件11径向延伸的直线，穿过静叶片114上该点的径向线指沿基环件11径向延伸并穿过该点的直线。
在本实施例中，对于型面18倾斜设置的各静叶片114中：各静叶片114的头部型面18倾斜角大于或等于该静叶片114的头部型面18倾斜角。将各静叶片114的尾部型面18倾斜角设置大于或等于头部型面18倾斜角，可以气流流过静叶片114间流道15时，静叶片114逐步加强对气流的引导与调整，以改善流道15涡流，降低分离损失，进而降低气流能量损失，降低噪音。
在本实施例中，对于型面18倾斜设置的各静叶片114中：各静叶片114的型面18倾斜角由该静叶片114的头部至尾部呈逐渐增大设置，从而在气流流过该排静叶片114间流道15时，可以逐渐调整气流，以改善气流分离损失，降低能量损失，降低噪音。
在本实施例中，请参阅图9和图10，第二排静叶片13中：各静叶片114的头部型面18b倾斜角为Q1，各静叶片114的尾部型面18b倾斜角为Q2，Q2≥Q1。将第二排静叶片13中各静叶片114的尾部型面18b倾斜角Q1设置大于或等于头部型面18b倾斜角Q1，可以气流流过静叶片114间流道15b时，静叶片114逐步加强对气流的引导与调整，以改善流道15b涡流，降低分离损失，进而降低气流能量损失，降低噪音。
在本实施例中，请参阅图9和图10，第二排静叶片13中：Q1的取值范围为0度~30度，即各静叶片114的头部型面18b倾斜角Q1小于或等于30度，可以在气流进入静叶片114间流道15b时，避免气流转角调整过大，而导致较大的能量损失。Q2的取值范围为0度~40度，即各静叶片114的头部型面18b倾斜角Q2小于或等于40度，可以在气流流过静叶片114间流道15b时，避免对气流调整过大，而导致较大的能量损失。
在本实施例中，请参阅图9和图10，第二排静叶片13中：Q1的取值范围为12度~18度，以在气流进入静叶片114间流道15b时，可以更好的减少流动分离损失，降低噪音。Q2的取值范围为20度~35度，且Q2≥Q1。在气流流过静叶片114间流道15b时，更好的减少流动分离损失，降低能量损失，减小气动噪音。
在本实施例中，第二排静叶片13中：Q1的取值范围为0度~30度，以在气流进入静叶片114间流道15b时，避免气流转角调整过大，而导致较大的能量损失。Q2的取值范围为15度~40度，以在气流流过静叶片114间流道15b时，避免对气流调整过大，而导致较大的能量损失。
在本实施例中，请参阅图9，穿过各静叶片114头部之叶根17与基环件11轴线对应的平面和穿过该静叶片114尾部之叶根17与基环件11轴线对应的平面之间的夹角为该静叶片114的包角P。
在本实施例中，请参阅图9，相邻两排静叶片114中：上一排静叶片114中各静叶片114的包角大于或等于下一排静叶片114中各静叶片114的包角。将上一排静叶片114中各静叶片114的包角设置较大，可以更好的逐步引导气流流动，减小分离损失，提升扩压效果。
在本实施例中，请参阅图7，相邻两排静叶片114中：上一排静叶片114中各静叶片114的弦长La大于或等于下一排静叶片114中各静叶片114的弦长Lb；由于气流进入扩压器10时，具有较大的周向速度，则在气流流经各排静叶片114时，将上一排静叶片114中各静叶片114的弦长Lb设置较长，可以更好的引导气流，减小气流的周向速度，并通过各排静叶片114逐步引导，降低分离损失。
在本实施例中，请参阅图13，穿过基环件11轴向的平面为该扩压器10的子午面，各静叶片114沿基环件11周向投影到子午面上为该静叶片114的子午投影面。各静叶片114的前缘线214为该静叶片114头部投影到子午面上的线段。各静叶片114的后缘线215为该静叶片114尾部投影到子午面上的线段。基环件11的径向面与子午投影面的交线为垂直于基环件11轴向的线段。
在本实施例中，至少一排静叶片114中：各静叶片114的前缘线214倾斜于基环件11的径向面设置。即该排静叶片114中各静叶片114前缘线214于子午投影面上的线段倾斜于基环件11的径向；从而可以减小流动分离损失，提升扩压效果。
在本实施例中，当扩压器10包括多排静叶片114时，可以将其中一排静叶片114中各静叶片114的前缘线214倾斜于基环件11的径向面设置。当然也可以将其中几排静叶片114中各静叶片114的前缘线214倾斜于基环件11的径向面设置。还可以将各排静叶片114中各静叶片114的前缘线214倾斜于基环件11的径向面设置。
在本实施例中，请参阅图13，第二排静叶片13中：各所述静叶片114的前缘线214与所述基环件11径向面的倾斜角B1的绝对值小于或等于25度。将第二排静叶片13中各静叶片114的前缘线214与基环件11径向面的倾斜角B1的绝对值小于或等于25度，以更好的减小流动分离损失，提升扩压效果。
在本实施例中，请参阅图13，第二排静叶片13中：各静叶片114的前缘线214朝向该静叶片114的尾部方向倾斜设置，以进一步调控叶根17附近的流动分离，减小流动分离损失，提升扩压效果。
在本实施例中，至少一排静叶片114中：各静叶片114的后缘线215倾斜于基环件11的径向面设置。即该排静叶片114中各静叶片114后缘线215于子午投影面上的线段倾斜于基环件11的径向；从而可以降低静叶片114出口处气流流动的不均匀性，提升扩压效果。
在本实施例中，当扩压器10包括多排静叶片114时，可以将其中一排静叶片114中各静叶片114的后缘线215倾斜于基环件11的径向面设置。当然也可以将其中几排静叶片114中各静叶片114的后缘线215倾斜于基环件11的径向面设置。还可以将各排静叶片114中各静叶片114的后缘线215倾斜于基环件11的径向面设置。
在本实施例中，请参阅图13，第二排静叶片13中：各所述静叶片114的后缘线215与所述基环件11径向面的倾斜角B2的绝对值小于或等于30度。将第二排静叶片13中各静叶片114的后缘线215与基环件11径向面的倾斜角B2的绝对值小于或等于30度，以更好提升静叶片114出口处气流流动的均匀性，提升扩压效果。
在本实施例中，扩压器10还包括机壳（图未示），基环件11置于机壳中，各静叶片114位于基环件11与机壳之间。设置机壳，不仅可以起到保护各静叶片114的作用，而且可以使基环件11与机壳之间形成通道，以更好的限定气流流动的通道，保证该扩压器10在不同送风装置中使用性能的一致性。
在本实施例中，各静叶片114的顶面至少80%的区域与机壳的内表面相接触，即各静叶片114的叶尖16的至少80%的区域与机壳的内表面相接触，以更好的通过各静叶片114、基环件11与机壳来限定气流流通的流道15，进而更好的引导气流流动，以提升扩压效果。
在本实施例中，机壳、基环件11及各静叶片114是一体成型，以保证机壳与各静叶片114良好的连接，同时增加该扩压器10的强度。
在本实施例中，机壳可以单独制作，再将带有静叶片114的基环件11置于机壳中。
本实施例的扩压器10不仅可以良好的改善流道15涡流，降低分离损失，减小能量损失，提升增压效果，而且可以降低气动噪音；使用本实施例的扩压器10的送风装置，不仅可以产生较大的吸力，而且运行噪音较小。本实施例的扩压器10不仅可以应用于送风装置，而且可以应用在吸尘设备、抽油烟机、吹送风装置等电器中。
请参阅图15，本实施例还提供了一种送风装置20，该送风装置20包括机架221、叶轮31、风罩32、马达222和如上任一实施例所述的扩压器10；扩压器10安装于机架221中，叶轮31设于扩压器10的前端，风罩32罩于叶轮31上，且风罩32安装于机架221上，马达222安装于机架221中，马达222与叶轮31相连。该送风装置20通过使用上述实施例的扩压器10，可以减小能量损失，降低运行噪音，从而在相同功率下，可以产生更大的吸力。
在本实施例中，请参阅图15，基环件11中安装有轴承225，马达222的驱动轴224穿过轴承225与叶轮31相连，以便马达222更灵活地驱动叶轮31转动。
在本实施例中，请参阅图15，叶轮31为闭式离心叶轮31a。在本实施例中，叶轮31也可以为开式离心叶轮。在本实施例中，请参阅图11，叶轮31还可以为混流式叶轮31b。
在本实施例中，请参阅图16，风罩32可以延伸到扩压器10的尾部，即风罩32同时罩住叶轮31和扩压器10，以更好的将叶轮31的出口的气流引导到扩压器10。
在本实施例中，机架221可以与风罩32一体成型，以保证机架221与风罩32的连接强度。
本实施例的送风装置20可以应用在吸尘设备、抽油烟机、吹送风装置、风扇等电器中。
本实施例还本实施例还公开了一种吸尘设备，包括如上任一实施例所述的送风装置20。本实施例的吸尘设备，使用了上述送风装置20，不仅功率大，效率高，而且噪音小。
实施例3
本实施例有别于实施例2之处在于：请参阅图6、图9和图10，在多排静叶片114中：至少一排静叶片114中的各静叶片114的型面18朝向该静叶片114的一侧倾斜设置。将相应静叶片114的型面18朝向该静叶片114的一侧倾斜，即该静叶片114的型面18高度方向倾斜于基环件11径向设置，可以有效改善气流离开静叶片114时，边界层分离，减少分离损失，改善静叶片114间流道15的涡流，进而降低流动损失，降低气流能量损失，降低气动噪音。
在本实施例中，可以将第一排静叶片12中各静叶片114的型面18a倾斜设置，从而在气流经过第一排静叶片12时，降低气流绝对速度的同时，减少分离损失，提升增压效果。
在本实施例中，请参阅图6和图8，可以将第二排静叶片13中各静叶片114的型面18b倾斜设置，从而在气流经过第二排静叶片13时，降低气流绝对速度，减少分离损失，提升增压效果。
在本实施例中，可以将第一排静叶片12中各静叶片114和第二排静叶片13中各静叶片114的型面18均倾斜设置，以更好的降低气流速度与减小分离损失，降低气流的不均匀度，提升增压效果。
在本实施例中，当扩压器10包括多排静叶片114时，可以将其中一排静叶片114中各静叶片114的型面18倾斜设置。当然也可以将其中几排静叶片114中各静叶片114的型面18倾斜设置。还可以将各排静叶片114中各静叶片114的型面18均倾斜设置。
在本实施例中，对于型面18倾斜设置的各静叶片114中：所述静叶片114的型面18朝向该静叶片114的吸力面19的一侧倾斜设置。可以更好的改善气流边界层分离，改善静叶片114间流道15的涡流，降低能量损失，降低气动噪音。
在本实施例中，第一排静叶片12中各静叶片114的型面18a倾斜设置时，该第一排静叶片12中各静叶片114的型面18a朝向该静叶片114的吸力面19a的一侧倾斜设置。
在本实施例中，请参阅图6和图9，第二排静叶片13中各静叶片114的型面18b倾斜设置时，该第二排静叶片13中各静叶片114的型面18朝向该静叶片114的吸力面19b的一侧倾斜设置。
在本实施例中，对于型面18倾斜设置的各静叶片114中：所述静叶片114的型面18朝向该静叶片114的压力面14的一侧倾斜设置。可以更好的改善气流的不均匀性，改善静叶片114间流道15的涡流，降低能量损失，降低气动噪音。
在本实施例中，第一排静叶片12中各静叶片114的型面18a倾斜设置时，该第一排静叶片12中各静叶片114的型面18a朝向该静叶片114的压力面14a的一侧倾斜设置。
在本实施例中，请参阅图6和图9，第二排静叶片13中各静叶片114的型面18b倾斜设置时，该第二排静叶片13中各静叶片114的型面18朝向该静叶片114的压力面14b的一侧倾斜设置。
以上仅为本申请的较佳实施例而已，并不用以限制本申请，凡在本申请的精神和原则之内所作的任何修改、等同替换和改进等，均应包含在本申请的保护范围之内。

Claims (58)

  1. 一种扩压器，其特征在于：包括基环件和多排静叶片，各排所述静叶片依序沿所述基环件的轴向设置于所述基环件的外环壁上，并均沿所述基环件的周向排布，所述基环件沿其轴向的相对两侧分别为进风侧和出风侧，自所述进风侧至所述出风侧，其中一排所述静叶片的弦长大于或等于与该排所述静叶片相邻的下一排所述静叶片的弦长；
    所述静叶片具有安装角，自所述进风侧至所述出风侧，其中一排所述静叶片的安装角小于或等于与该排所述静叶片相邻的下一排所述静叶片的安装角。
  2. 根据权利要求1所述的扩压器，其特征在于：所述静叶片的头部具有入口安放角，自所述进风侧至所述出风侧，其中一排所述静叶片的所述入口安放角小于或等于与该排所述静叶片相邻的下一排所述静叶片的所述入口安放角。
  3. 根据权利要求2所述的扩压器，其特征在于：所述静叶片的尾部具有出口安放角，自所述进风侧至所述出风侧，其中一排所述静叶片的所述出口安放角小于或等于与该排所述静叶片相邻的下一排所述静叶片的所述出口安放角。
  4. 根据权利要求3所述的扩压器，其特征在于：自所述进风侧至所述出风侧，其中一排所述静叶片的所述出口安放角小于或等于与该排所述静叶片相邻的下一排所述静叶片的所述入口安放角；或者，其中一排所述静叶片的所述出口安放角大于或等于与该排所述静叶片相邻的下一排所述静叶片的所述入口安放角。
  5. 根据权利要求4所述的扩压器，其特征在于：所述扩压器包括第一排静叶片和第二排静叶片，所述第一排静叶片和所述第二排静叶片自所述进风侧至所述出风侧依序沿所述基环件的轴向设置于所述基环件的外环壁上。
  6. 根据权利要求5所述的扩压器，其特征在于：所述第一排静叶片的入口安放角的角度值为5°~20°，所述第二排静叶片的入口安放角的角度值为20°~40°。
  7. 根据权利要求5所述的扩压器，其特征在于：所述第一排静叶片的出口安放角的角度值为10°~60°，所述第二排静叶片的出口安放角的角度值为60°~80°。
  8. 根据权利要求5所述的扩压器，其特征在于：所述第一排静叶片的弦长和所述第二排静叶片的弦长之比大于等于1，且小于等于5。
  9. 根据权利要求5所述的扩压器，其特征在于：所述第一排静叶片的叶片数小于或等于所述第二排静叶片的叶片数，所述第一排静叶片和所述第二排静叶片各自延所述外环壁的周向均匀分布，所述第一排静叶片和所述第二排静叶片于所述外环壁的轴向相互错位分布，至少所述第一排静叶片中的一个静叶片的头部或尾部与所述第二排静叶片中的一个静叶片的头部或尾部于所述外环壁的轴向对齐。
  10. 根据权利要求9所述的扩压器，其特征在于：所述第一排静叶片的叶片数为6片~20片，所述第二排静叶片的叶片数为10片~30片。
  11. 根据权利要求5所述的扩压器，其特征在于：所述第一排静叶片的头部和所述第二排静叶片的尾部之间的沿所述基环件轴向的间距小于等于3mm。
  12. 根据权利要求3~11任一项所述的扩压器，其特征在于：所述出口安放角包括位于所述静叶片的叶根处的第一出口安放角和位于所述静叶片的叶顶处的第二出口安放角，所述第一出口安放角的角度值和所述第二出口安放角的角度值的差值为0°~20°。
  13. 根据权利要求1所述的扩压器，其特征在于：所述静叶片为弧形叶片。
  14. 一种扩压器，其特征在于：包括基环件和多个静叶片，多个所述静叶片沿所述基环件的轴向依次设置呈多排，且各排静叶片中所述静叶片数量为多个，各排静叶片中多个所述静叶片沿所述基环件周向设置，所述基环件的横截面呈圆形；多排所述静叶片中至少一排静叶片中的各所述静叶片的厚度由该静叶片的头部至尾部呈非恒定设置。
  15. 根据权利要求14所述的扩压器，其特征在于，厚度非恒定设置的各所述静叶片中：各所述静叶片的厚度由该静叶片的头部至尾部呈先逐渐增大再逐渐减小。
  16. 根据权利要求15所述的扩压器，其特征在于，厚度非恒定设置的各所述静叶片中：各所述静叶片厚度最大处的位置弦长为该静叶片弦长的30%~45%。
  17. 根据权利要求14所述的扩压器，其特征在于，第二排静叶片中各所述静叶片中线上各点对应的厚度满足如下关系：
    各所述静叶片头部的厚度范围为0.1-0.8mm；
    各所述静叶片位置弦长为该静叶片弦长的40%处的厚度范围为1.1-1.4mm；
    各所述静叶片尾部的厚度范围为0.1-1mm。
  18. 根据权利要求14所述的扩压器，其特征在于，第二排静叶片中：各所述静叶片中线上各点对应厚度Hb满足如下公式：
    T2≤Hb≤T1；
    T1=0.82+0.68L1b-0.17L1b 2+0.011L1b 3；
    T2=0.68L1b-0.17L1b 2+0.011L1b 3；
    其中，L1b为所述静叶片中线上对应点到该静叶片头部的距离，L1b 2为L1b的平方，L1b 3为L1b的3次方，T1为所述静叶片中线上对应点处的最大厚度关系式，T2为所述静叶片中线上对应点处的最小厚度关系式。
  19. 根据权利要求18所述的扩压器，其特征在于，第二排静叶片中：各所述静叶片中线上各点对应厚度Hb满足如下公式：
    Hb=0.32+0.68L1b-0.17L1b 2+0.011L1b 3。
  20. 根据权利要求14所述的扩压器，其特征在于，厚度非恒定设置的各所述静叶片中：各所述静叶片中线上任意位置对应叶根与叶尖厚度分别为H1和H2，H1≥H2。
  21. 根据权利要求20所述的扩压器，其特征在于：0≤H1-H2≤0.5mm。
  22. 根据权利要求14所述的扩压器，其特征在于，至少一排所述静叶片中：各所述静叶片的前缘线倾斜于所述基环件的径向面设置。
  23. 根据权利要求22所述的扩压器，其特征在于：第二排所述静叶片中：各所述静叶片的前缘线与所述基环件径向面的倾斜角的绝对值小于或等于25度。
  24. 根据权利要求14所述的扩压器，其特征在于，至少一排所述静叶片中：各所述静叶片的后缘线倾斜于所述基环件的径向面设置。
  25. 根据权利要求23所述的扩压器，其特征在于：第二排所述静叶片中：各所述静叶片的前缘线与所述基环件径向面的倾斜角的绝对值小于或等于30度。
  26. 根据权利要求14所述的扩压器，其特征在于，相邻两排所述静叶片中：上一排静叶片中各所述静叶片的弦长大于或等于下一排静叶片中各所述静叶片的弦长。
  27. 根据权利要求14所述的扩压器，其特征在于，相邻两排所述静叶片中：下一排静叶片中静叶片的数量为上一排静叶片中静叶片数量的1.5~3倍。
  28. 根据权利要求14所述的扩压器，其特征在于，相邻两排所述静叶片中：上一排静叶片中各所述静叶片的包角大于或等于下一排静叶片中各所述静叶片的包角。
  29. 根据权利要求14所述的扩压器，其特征在于，相邻两排所述静叶片中：上一排静叶片中各所述静叶片的尾部与邻近的下一排相应所述静叶片的头部对齐设置。
  30. 根据权利要求14所述的扩压器，其特征在于，相邻两排所述静叶片中：上一排静叶片中各所述静叶片的尾部沿所述基环件的周向偏离邻近的下一排相应所述静叶片的头部角度小于或等于20度。
  31. 根据权利要求14所述的扩压器，其特征在于：各所述静叶片上各处的安装角由该静叶片的头部至尾部呈逐渐增大设置。
  32. 根据权利要求14所述的扩压器，其特征在于：各所述静叶片的入口安放角沿所述基环件的径向变化幅度小于或等于10度，且各所述静叶片叶根处的入口安放角大于或等于该静叶片叶尖处的入口安放角。
  33. 根据权利要求14所述的扩压器，其特征在于：所述扩压器还包括机壳，所述基环件置于所述机壳中，各所述静叶片位于所述基环件与所述机壳之间。
  34. 根据权利要求33所述的扩压器，其特征在于：各所述静叶片的顶面至少80%的区域与所述机壳的内表面相接触。
  35. 一种扩压器，其特征在于：包括基环件和多个静叶片，多个所述静叶片沿所述基环件的轴向依次设置呈多排，且各排静叶片中所述静叶片数量为多个，各排静叶片中多个所述静叶片沿所述基环件周向设置，所述基环件的横截面呈圆形；多排所述静叶片中至少一排静叶片中的各所述静叶片的型面朝向该静叶片的一侧倾斜设置。
  36. 根据权利要求35所述的扩压器，其特征在于，型面倾斜设置的各所述静叶片中：所述静叶片的型面朝向该静叶片的吸力面的一侧倾斜设置。
  37. 根据权利要求36所述的扩压器，其特征在于：各所述静叶片的尾部型面倾斜角大于或等于该静叶片的头部型面倾斜角。
  38. 根据权利要求35所述的扩压器，其特征在于：第二排中各所述静叶片的型面朝向该静叶片的吸力面的一侧倾斜设置。
  39. 根据权利要求38所述的扩压器，其特征在于，第二排所述静叶片中：各所述静叶片的头部型面倾斜角为Q1，各所述静叶片的尾部型面倾斜角为Q2，Q1的取值范围为0度~30度；Q2的取值范围为0度~40度。
  40. 根据权利要求35所述的扩压器，其特征在于，型面倾斜设置的各所述静叶片中：所述静叶片的型面朝向该静叶片的压力面的一侧倾斜设置。
  41. 根据权利要求35所述的扩压器，其特征在于，型面倾斜设置的各所述静叶片中：各所述静叶片的型面倾斜角由该静叶片的头部至尾部呈逐渐增大设置。
  42. 根据权利要求35所述的扩压器，其特征在于，至少一排所述静叶片中：各所述静叶片的前缘线倾斜于所述基环件的径向面设置。
  43. 根据权利要求42所述的扩压器，其特征在于：第二排所述静叶片中：各所述静叶片的前缘线与所述基环件径向面的倾斜角的绝对值小于或等于25度。
  44. 根据权利要求35所述的扩压器，其特征在于，至少一排所述静叶片中：各所述静叶片的后缘线倾斜于所述基环件的径向面设置。
  45. 根据权利要求44所述的扩压器，其特征在于：第二排所述静叶片中：各所述静叶片的前缘线与所述基环件径向面的倾斜角的绝对值小于或等于30度。
  46. 根据权利要求35所述的扩压器，其特征在于，相邻两排所述静叶片中：上一排静叶片中各所述静叶片的弦长大于或等于下一排静叶片中各所述静叶片的弦长。
  47. 根据权利要求35所述的扩压器，其特征在于，相邻两排所述静叶片中：下一排静叶片中静叶片的数量为上一排静叶片中静叶片数量的1.5~3倍。
  48. 根据权利要求35所述的扩压器，其特征在于，相邻两排所述静叶片中：上一排静叶片中各所述静叶片的包角大于或等于下一排静叶片中各所述静叶片的包角。
  49. 根据权利要求35所述的扩压器，其特征在于，相邻两排所述静叶片中：上一排静叶片中各所述静叶片的尾部与邻近的下一排相应所述静叶片的头部对齐设置。
  50. 根据权利要求35所述的扩压器，其特征在于，相邻两排所述静叶片中：上一排静叶片中各所述静叶片的尾部沿所述基环件的周向偏离邻近的下一排相应所述静叶片的头部角度小于或等于20度。
  51. 根据权利要求35所述的扩压器，其特征在于：各所述静叶片上各处的安装角由该静叶片的头部至尾部呈逐渐增大设置。
  52. 根据权利要求35所述的扩压器，其特征在于：各所述静叶片的入口安放角沿所述基环件的径向变化幅度小于或等于10度，且各所述静叶片叶根处的入口安放角大于或等于该静叶片叶尖处的入口安放角。
  53. 根据权利要求35所述的扩压器，其特征在于，第二排所述静叶片中：各所述静叶片的入口安放角的范围为20度~60度。
  54. 根据权利要求35所述的扩压器，其特征在于，第二排所述静叶片中：各所述静叶片的出口安放角的范围为50度~90度。
  55. 根据权利要求35所述的扩压器，其特征在于：所述扩压器还包括机壳，所述基环件置于所述机壳中，各所述静叶片位于所述基环件与所述机壳之间。
  56. 根据权利要求55所述的扩压器，其特征在于：各所述静叶片的顶面至少80%的区域与所述机壳的内表面相接触。
  57. 一种送风装置，其特征在于：包括权利要求1、14或35任一项所述的扩压器。
  58. 一种吸尘设备，其特征在于：包括权利要求57所述的送风装置。
PCT/CN2020/137650 2020-01-06 2020-12-18 扩压器、送风装置及吸尘设备 WO2021139508A1 (zh)

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