WO2019035493A1 - Ventilateur radial - Google Patents

Ventilateur radial Download PDF

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Publication number
WO2019035493A1
WO2019035493A1 PCT/KR2017/008867 KR2017008867W WO2019035493A1 WO 2019035493 A1 WO2019035493 A1 WO 2019035493A1 KR 2017008867 W KR2017008867 W KR 2017008867W WO 2019035493 A1 WO2019035493 A1 WO 2019035493A1
Authority
WO
WIPO (PCT)
Prior art keywords
inlet
blades
blade
shroud
radial fan
Prior art date
Application number
PCT/KR2017/008867
Other languages
English (en)
Korean (ko)
Inventor
이동경
변효석
김상각
Original Assignee
주식회사 에스 피 지
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 주식회사 에스 피 지 filed Critical 주식회사 에스 피 지
Publication of WO2019035493A1 publication Critical patent/WO2019035493A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes

Definitions

  • the present invention relates to a radial fan, more particularly, to a radial fan having excellent mechanical stability and improved air flow.
  • Radial blowers are used in a wide range of applications including industrial, electronic, and personal applications.
  • Other air-positive pressure devices such as, for example, cooling devices such as fans for cooling electronic components or providing air conditioning, and filtration devices often include radial blowers.
  • Such a blower typically has a central inlet and an impeller that draws air through the inlet as it is rotated by the motor and pushes the air in a circular direction.
  • Scrolls often provide a housing for blower components and include air passageways that wrap around the perimeter of the impeller. The impeller can push air out of the outlet through the air passage.
  • the shape and size of the scroll, the impeller design and size, the motor speed and output, and the fluid density both affect the efficiency and power of the radial blower.
  • the design of a radial blower is driven by efficiency and power requirements, and shape and size are not important limiting factors.
  • the size and shape of the blower may be particularly limited by ergonomic and transport considerations.
  • blowers fans
  • a radial fan which improves the area of an air flow channel to optimize performance and efficiency of the fan.
  • It also provides a radial fan that optimizes the position of the blades and improves the shape of the blades to reduce mechanical stability and noise generation.
  • a radial fan including a shroud having an inlet, a hub spaced apart from the shroud, a plurality of first blades radially distributed with respect to the inlet, A plurality of second blades radially shorter than the first blades and disposed radially between the first blades and radially distributed about the inlet, a plurality of channels being formed between the plurality of first blades , The channels guide the air introduced through the inlet port and discharge the air through the outlet port.
  • the first blade forms a bend in the rotation direction and a bend in the rotation direction opposite to the rotation direction.
  • the second blade forms a bend in the rotational direction and a bend in the opposite rotational direction.
  • the plurality of second blade positions are randomly arranged in the rotating direction with respect to the center of the inlet port.
  • the first blade and the second blade are coupled between the shroud and the hub.
  • the width of the first blade is narrowed from the inlet side toward the outlet side.
  • the width of the second blade is narrowed from the inlet side toward the outlet side.
  • the shroud forms an inclination from the inlet toward the outlet.
  • the hub has a center hole coupled to a rotary shaft at the center, and the center hole is curved convexly in the shroud direction.
  • the inlet side surface area of the channels is set to be 1.5 to 2 times or less of the surface area of the channels on the side of the discharge port, according to an embodiment of the present invention.
  • a radial fan according to an embodiment of the present invention is an integral molded part made of a composite material, wherein the molded part is prevented from generating static electricity during operation or is discharged.
  • the present invention can optimize the performance and efficiency of the fan by improving the area of the air flow channel. Further, the optimum position of the blade can be selected, and the shape of the blade can be improved to reduce mechanical stability and noise generation. Further, the combination of the impeller, the shroud, and the hub can facilitate fabrication.
  • the optimum position of the blade can be selected, and the shape of the blade can be improved to reduce mechanical stability and noise generation.
  • the combination of the impeller, the shroud, and the hub can facilitate fabrication.
  • FIG. 1 is a perspective view of a radial fan according to an embodiment.
  • FIG. 2 is a view for explaining an impeller design of a radial fan according to an embodiment.
  • FIG 3 is a cross-sectional view of a radial fan according to an embodiment.
  • FIG. 4 is a longitudinal sectional view of the radial fan according to the embodiment.
  • FIG 5 is a view showing the channel area of the radial fan according to the embodiment.
  • first, second, A, B, (a), and (b) may be used. These terms are intended to distinguish the constituent elements from other constituent elements, and the terms do not limit the nature, order or order of the constituent elements.
  • FIG. 1 is a perspective view of a radial fan according to an embodiment of the present invention
  • FIG. 2 is a view for explaining a design of a radial fan according to an embodiment
  • FIG. 3 is a longitudinal sectional view of a radial fan
  • FIG. 4 is a cross-sectional view of a radial fan according to an embodiment of the present invention
  • FIG. 5 is a view showing a channel area of a radial fan according to an embodiment.
  • the radial fan includes a shroud 100 having an inlet 110, a hub 200 spaced apart from the shroud 100, and a radial fan
  • a plurality of distributed first blades 300 are radially shorter than the first blades 300 and are disposed between a plurality of the first blades 300 and are radially distributed with respect to the inlet 110
  • a plurality of channels 500 are formed between a plurality of second blades 400 and a plurality of the first blades 300. The channels 500 guide the air introduced through the inlet 110 And discharges to the outside through the discharge port (600).
  • the radial fan belongs to the low speed fan of the fan, and relatively high pressure is applied to the radial fan, the flow resistance is relatively large as in the fan unit, which is a part of the domestic boiler facilities, It can be applied.
  • the shroud 100 is a donut-shaped circular disk having a hole at the center, and the center hole 210 may form an inlet 110 into which air flows.
  • the shroud 100 may be inclined from the inlet 110 toward the outlet 600.
  • a plurality of first blades 300 and a plurality of second blades 400 are provided under the shroud 100.
  • a plurality of first blades 300 and a plurality of second blades 400 are provided with a hub And a channel 500 through which the air flows is formed by the shroud 100, the first blade 300, the second blade 400, and the hub 200.
  • the first blade 300 and the second blade 400 may be coupled between the shroud 100 and the hub 200.
  • a plurality of the first blades 300 may bend in the rotational direction and bend in the opposite rotational direction. Specifically, a plurality of first blades 300 are partially formed in a first direction in a rotational direction of the radial fan starting from one side, and a second bending in a direction opposite to the rotation of the radial fan And extend to the other side. In other words, the plurality of first blades 300 extend in the radial direction at the center of the radial fan, and can form an 'S' shaped double bend.
  • the plurality of second blades 400 may have a shorter length than the first blades 300 in the radial direction and may bend in the rotational direction and bend in the opposite rotational direction. Specifically, a plurality of the second blades 400 are partially formed in a first direction in a rotational direction of the radial fan starting from one side, and at a portion where the first bending ends, To the other side. In other words, the plurality of second blades 400 are formed to have a shorter length than the first blades 300 and extend in the radial direction, and can form an 'S' shaped double bend.
  • first blades 300 may be arranged with a predetermined distance in the circumferential direction, and the second blades 400 may be positioned between the two first blades 300.
  • the positions of the plurality of second blades 400 may be randomly arranged in the circumferential direction with respect to the center of the inlet 110.
  • the radial fan is provided with an impeller constituted by a backward blade.
  • the main design variables include a cord length, a blade thickness, and a blade number, which are airfoil variables.
  • the impeller shape parameters include an inlet angle, , Inlet height, and outlet height. Therefore, the impeller of the radial fan can be expressed in a two-dimensional shape in which the two-dimensional blades are piled up in the height direction.
  • the impeller may include the first blade 300 and the second blade 400.
  • Impeller is used. That is, in the two-dimensional impeller, the stream surface around the blade is plane, while the stream surface around the blade has a curvature in the three-dimensional impeller, and the air flow toward the inlet port 110 is in the direction of the rotation axis And the air flow on the side of the discharge port 600 may have a generally radial direction.
  • Equation 1 is as follows.
  • specific speed is a non-dimensional variable representing a specific fan, and it is a frequently used parameter for comparing characteristics of fan, type, selection of impeller, and comparison of the same fan type.
  • the fan has a larger amount of air than the pressure rise amount. If the non-velocity is small, the pressure increase amount of the fan is higher than the air amount. Also, the impeller having a large non-velocity has a larger impeller outlet width than the diameter of the outlet, and the impeller having a smaller specific velocity may have a narrow outlet width.
  • the specific velocity is about 100 to 1000. In the case of 100 to 400, the specific speed is relatively low, and the case where the specific speed is 400 to 700 is mainly used.
  • the specific diameter, ⁇ can be used as a good measure to determine the size (diameter) of the impeller during design.
  • Equation 2 The pressure rise of the impeller and the work by the Euler equation have the relationship expressed by Equation 2 below.
  • Equation 2 is as follows.
  • the velocity component at the impeller outlet ( ) And the diameter of the impeller outlet can be determined.
  • the flow from the impeller does not flow along the exit wing and slip occurs, so the outlet wing angle should be larger than the flow angle.
  • Angle Lt; RTI ID 0.0 > ⁇ , < / RTI > And the angle of the exit wing can be calculated from the following equation (3).
  • Equation 3 is as follows.
  • the slip coefficient is expressed by the following Equation 4 using the Stodola equation.
  • Equation 4 is as follows.
  • the operating Mach numbers of most blowers are 0.1 to 0.3, they can be assumed to be incompressible flows.
  • the inflow flow to the first blade 300 is inevitably made nonuniform due to the wake of the installed structure, and the resulting unsteady flow around the wing contributes to noise radiation.
  • the boundary layer around the rotating car is mainly a turbulent boundary layer, which ultimately causes very strong noise emission at the trailing edge of the first blade 300. Therefore, the noise in the radial fan is classified into inflow-turbulence noise, trailing edge noise, inflow vortex noise, and blunt-trailing edge noise. .
  • the most influential factor for the radial fan noise is the rear-end noise of the wing, and the turbulence around the impeller itself can not radiate a large amount of sound.
  • the turbulence caused by the quadrupole noise meets the rear end of the wing, .
  • a load (load) acting on the blade is a major cause of the radial fan noise.
  • the most dominant of the unsteady load noises in the rotational and axial directions is the noise due to the load in the rotational direction.
  • the width of the first blade 300 decreases from the inlet 110 toward the outlet 600 and the width of the second blade 400 decreases from the inlet 110 toward the outlet 600. [ The width can be narrowed toward the discharge port 600 side.
  • the hub 200 is formed with a center hole 210 coupled to a rotating shaft at a center thereof and the center hole 210 can be curved convexly toward the inlet 110.
  • the hub 200 is formed in a disc shape in the circumferential direction about the rotation axis, and the center portion may be curved convexly toward the shroud 100.
  • the channel 500 is formed between two or more first blades 300 and has a plurality of circumferential radial shapes.
  • the air introduced through the inlet 110 is discharged to the outside through the outlet 600 To guide the air flow.
  • the second blade 400 is randomly disposed in a predetermined space in which the channel 500 is formed, and the space in the channel 500 can be divided into two parts by the second blade 400.
  • the entrance angle of the channel 500 is not constant and varies for each rotational direction position, whereby reducing the air flow separation and slip between the channels 500 and allowing the phase of the air vortices passing through the channel 500 to be canceled.
  • the surface area of the channels 500 on the side of the discharge port 600 may be 1.5 to 2 times or less.
  • the number of openings of the channel 500 by the second blades 400 may be 0.5 times the number of openings of the channel 500.
  • the second blades 400 may be disposed in the channel 500, but may not be disposed at regular intervals, but may be randomly disposed. Accordingly, since the phase of the second blade 400 is the same as the load applied to the second blade 400, the phase 1 is not constant, and the actual distance decreases as the average load decreases, so that the load noise can be reduced. However, as the repetitive phase? 2 increases, the effect of clogging one channel 500 appears and performance degradation is expected. Therefore, it may be required to use phases ( ⁇ 1, ⁇ 2) within about 5 °.
  • the radial fan is an integral molded part made of a composite material, and the molded part can prevent static electricity from being generated during operation or can be discharged.
  • the shroud 100 and the hub 200 of the radial fan may be formed so that a circular shape is symmetrically formed in a circumferential direction about the rotation axis.
  • the first blades 300 and the second blades 400 may be formed by directly forming the molded shroud 100 and the hub 200 on the entire length of the first blade 300 and the second blade 400, To be formed completely.
  • the radial fan according to the embodiment of the present invention is guided from the air flow and the inlet of the channel to the channel between the first and second blades 400, and the flow of the channel to the second blade 400 And the position of the second blade 400 is adjusted so as to improve the high efficiency condition in which the slip and the flow separation loss are reduced and the peak peak noise of the rear end of the first blade 300 due to the repeated load of the first blade 300
  • the torque balance is not constant in the circumferential direction, and noise reduction is achieved.
  • the present invention can optimize the performance and efficiency of the fan by improving the area of the air flow channel. Further, the optimum position of the blade can be selected, and the shape of the blade can be improved to reduce mechanical stability and noise generation. Further, the combination of the impeller, the shroud, and the hub can facilitate fabrication.

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

Abstract

La présente invention concerne un ventilateur radial et, plus particulièrement, un ventilateur radial présentant une excellente stabilité mécanique et un écoulement d'air amélioré. Le ventilateur radial comprend : une chemise comportant une entrée ; un moyeu agencé pour être espacé de la chemise ; une pluralité de premières pales réparties radialement autour de l'entrée ; une pluralité de secondes pales, plus courtes que les premières pales dans la direction radiale, étant respectivement agencées entre la pluralité de premières pales et réparties radialement autour de l'entrée ; et une pluralité de canaux formés respectivement entre la pluralité de premières pales, les canaux guidant l'air entrant à travers l'entrée de façon à permettre l'évacuation de l'air vers l'extérieur à travers un orifice d'évacuation.
PCT/KR2017/008867 2017-08-14 2017-08-16 Ventilateur radial WO2019035493A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR20170103066 2017-08-14
KR10-2017-0103066 2017-08-14

Publications (1)

Publication Number Publication Date
WO2019035493A1 true WO2019035493A1 (fr) 2019-02-21

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PCT/KR2017/008867 WO2019035493A1 (fr) 2017-08-14 2017-08-16 Ventilateur radial

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110905850A (zh) * 2019-10-28 2020-03-24 天津怡和嘉业医疗科技有限公司 用于通气治疗设备的叶轮、风机以及通气治疗设备

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH074389A (ja) * 1993-06-17 1995-01-10 Hitachi Ltd ターボファン及びターボファンを搭載した装置
JPH09209984A (ja) * 1996-02-02 1997-08-12 Japan Servo Co Ltd 循環式ポンプの羽根車
US20070014666A1 (en) * 2005-07-12 2007-01-18 Robert Bosch Corporation Centrifugal fan assembly
KR20120129892A (ko) * 2010-02-05 2012-11-28 카메론 인터내셔널 코포레이션 원심 압축기에서의 디퓨저의 소날개
US20130183155A1 (en) * 2012-01-17 2013-07-18 Adrian L. Stoicescu Fuel system centrifugal boost pump impeller

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH074389A (ja) * 1993-06-17 1995-01-10 Hitachi Ltd ターボファン及びターボファンを搭載した装置
JPH09209984A (ja) * 1996-02-02 1997-08-12 Japan Servo Co Ltd 循環式ポンプの羽根車
US20070014666A1 (en) * 2005-07-12 2007-01-18 Robert Bosch Corporation Centrifugal fan assembly
KR20120129892A (ko) * 2010-02-05 2012-11-28 카메론 인터내셔널 코포레이션 원심 압축기에서의 디퓨저의 소날개
US20130183155A1 (en) * 2012-01-17 2013-07-18 Adrian L. Stoicescu Fuel system centrifugal boost pump impeller

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110905850A (zh) * 2019-10-28 2020-03-24 天津怡和嘉业医疗科技有限公司 用于通气治疗设备的叶轮、风机以及通气治疗设备

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