WO2022077585A1 - 一种叶轮、应用有该叶轮的离心风机和吸油烟机 - Google Patents

一种叶轮、应用有该叶轮的离心风机和吸油烟机 Download PDF

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Publication number
WO2022077585A1
WO2022077585A1 PCT/CN2020/124782 CN2020124782W WO2022077585A1 WO 2022077585 A1 WO2022077585 A1 WO 2022077585A1 CN 2020124782 W CN2020124782 W CN 2020124782W WO 2022077585 A1 WO2022077585 A1 WO 2022077585A1
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Prior art keywords
impeller
disc
blade
chord length
line segment
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PCT/CN2020/124782
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English (en)
French (fr)
Inventor
雷改
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宁波方太厨具有限公司
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Publication of WO2022077585A1 publication Critical patent/WO2022077585A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
    • F04D29/283—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis rotors of the squirrel-cage type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • 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
    • 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
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/663—Sound attenuation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24C—DOMESTIC STOVES OR RANGES ; DETAILS OF DOMESTIC STOVES OR RANGES, OF GENERAL APPLICATION
    • F24C15/00—Details
    • F24C15/20—Removing cooking fumes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/304—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the trailing edge of a rotor blade

Definitions

  • the invention relates to the technical field of oil fume purification devices, in particular to an impeller and a centrifugal fan applied with the impeller, and also relates to a range hood applied with the centrifugal fan.
  • Range hoods have become one of the indispensable kitchen appliances in modern homes.
  • the range hood uses the principle of fluid dynamics to work.
  • the centrifugal fan installed inside the range hood sucks and discharges the oil fume, and uses the filter screen to filter some grease particles.
  • the centrifugal fan includes a volute, an impeller installed in the volute, and a motor that drives the impeller to rotate. When the impeller rotates, a negative pressure suction is generated in the center of the fan, and the oil fume under the range hood is sucked into the fan. After being accelerated by the fan, it is collected by the volute and guided out of the room.
  • an ultra-thin top-suction range hood disclosed in Chinese patent CN207006315U (patent number 201720917014.9) includes at least a casing and an air supply structure.
  • the motor and the wind wheel, the fan volute includes a front cover plate with an air inlet and an intermediate ring wall, and the intermediate ring wall vertically connects the front cover plates with a continuous and smooth transition surface to form an inner flow channel with an upper opening and Outlet.
  • the air inlet and air outlet of the fan system are in the same direction, causing the fluid to enter the volute in the fan system with a 90-degree turn. After turning 90 degrees, it can be discharged through the air outlet.
  • the noise and energy loss to the fluid are relatively large, resulting in significantly higher noise for the performance of the whole machine under the same air volume.
  • the number of forward impellers, but the efficiency is low) is the only one with low noise. Therefore, although the axial flow impeller and the mixed flow impeller are relatively more suitable for the flow field movement law of the range hood, due to the high noise of the impeller itself, through the test comparison, the noise of the multi-blade centrifugal impeller is still low under the same air volume.
  • Most of the multi-wing centrifugal impellers on the range hood are composed of front and rear discs, blades and wheel discs of the impeller.
  • the blades of this type of impeller are of equal chord length in the height direction. Since the front disc of the impeller is a plane structure, considering the dynamic balance of the impeller, there is a certain distance between the front cover disc of the impeller and the volute, where backflow is easy to occur. Furthermore, since the fluid enters the impeller in the axial direction from the collector, and the relative width of the multi-blade centrifugal impeller is relatively large, in the axial direction of the impeller, the airflow at the inlet of the fan impeller blade is inclined to the disk side as a whole.
  • the airflow at the outlet of the impeller is affected by the air intake and is unevenly distributed along the axial direction, resulting in a secondary vortex in the volute of the forward fan.
  • the airflow enters the impeller through the concentrator, forming a larger positive angle of attack, and the same impeller will generate a larger positive attack angle than that under large flow conditions when operating at a small flow rate.
  • Uneven distribution the flow rate of the blade channel near the upper cover plate is small, the positive attack angle is larger, the flow separation phenomenon in the blade channel is more obvious, and the flow separation phenomenon obviously causes the noise.
  • the first technical problem to be solved by the present invention is to provide an impeller that can reduce noise in view of the above-mentioned shortcomings of the prior art.
  • the second technical problem to be solved by the present invention is to provide a centrifugal fan using the above impeller.
  • the third technical problem to be solved by the present invention is to provide a range hood using the above centrifugal fan.
  • an impeller comprising a front disc, a rear disc and a blade arranged between the front disc and the rear disc, characterized in that the inlet installation angle of the blade is It gradually increases from the front disc to the rear disc along the axial direction of the impeller.
  • the size of the inlet installation angle of each position of the blade along the axial direction is in the range of 65° ⁇ 87°.
  • chord length of the blade at the front disc is L1
  • chord length of the blade at the rear disc is L2
  • the chord length of the blade gradually decreases from the front disc to the rear disc along the axial direction of the impeller, and the outer diameter of the impeller is is D2, the inner diameter of the impeller is D1, and satisfies L1: L2 ⁇ [15:14, 5:2], D1: D2 ⁇ [0.78, 0.88].
  • the impeller further includes a middle disk located between the front disk and the rear disk, the blades pass through the middle disk, the chord length of the blades at the front disk is L1, and the blades are at the rear
  • the chord length at the disk is L2
  • the chord length of the blade at the middle disk is L3, and the chord length of the blade gradually increases from the front disk to the middle disk along the axial direction of the impeller, and gradually decreases from the middle disk to the rear disk, so
  • the outer diameter of the impeller is D2
  • the inner diameter of the impeller is D1
  • the vane has an outlet end, and the outlet end of the vane is straight between the front disc and the middle disc and between the middle disc and the rear disc; or the outlet end of the vane is in the Between the front plate and the middle plate, and between the middle plate and the rear plate are curves, and the curves are Bezier curves or Archimedes spirals.
  • the chord length of the blade at the front disc is L1
  • the chord length of the blade at the rear disc is L2
  • the chord length of the blade gradually moves from the front disc to the rear disc along the axial direction of the impeller Increase
  • the outer diameter of the impeller is D2
  • the inner diameter of the impeller is D1
  • a gap is formed at the end of the blade connected to the front disc, and the gap is formed by concave from the inlet of each blade to the outlet direction, and the overall height of the blade is b, so The height of the gap is b1 and satisfies b1/b ⁇ [1/16B, 3/16B].
  • the profile of the notch includes a straight line segment and a curved segment connected in sequence, the starting point of the straight segment is close to the front plate, the end point of the straight segment is the same as the starting point of the curved segment, and the end point of the curved segment is far from the front plate.
  • the curved section is a smooth transition section.
  • the front end surface of the front disc is designed with a curved surface
  • the front end surface of the front disc is designed with a curved surface. It is gradually inclined toward the rear disk from the radially inner side to the radially outer side, and the inclined front end surface is a curve concave toward the inside of the impeller.
  • the profile line of the curved surface includes a first line segment, a second line and a third line segment that are smoothly connected in sequence from the inside to the outside in the radial direction, the first line segment is an arc-shaped transition segment, and the second line segment is an arc-shaped transition segment.
  • the line segment is a logarithmic spiral line segment with a variable helix angle, and the third line segment is a Bezier curve segment.
  • the technical solution adopted by the present invention to solve the above-mentioned second technical problem is: a centrifugal fan, which is characterized in that the above-mentioned impeller is applied.
  • the technical solution adopted by the present invention to solve the above-mentioned third technical problem is: a range hood, which is characterized in that: the above-mentioned centrifugal fan is applied.
  • the present invention has the advantages that: by setting the inlet installation angle gradually changing along the axial direction, the working force matches the gas flow rate, thereby improving the unevenness of the impeller outlet speed, and when applied to a fan, it can improve the The secondary vortex near the upper cover surface of the volute; by making the blade form a gap at the front disc to form a variable inner diameter structure, it can further improve the unevenness of the impeller outlet speed, and can also widen the blade path and increase the intake air volume;
  • the front end of the disc is designed with a curved surface.
  • the impeller When used in a fan, it can optimize the airflow backflow phenomenon at the gap between the front disc and the volute, and improve the working efficiency of the fan system; the impeller is a slanted impeller, which can reduce the flow separation area in the blade passage. , reducing the degree of flow separation, thereby reducing fluid noise.
  • FIG. 1 is a schematic structural diagram of an embodiment of a range hood of the present invention.
  • Fig. 3 is the structural representation of the first embodiment of the impeller of the present invention.
  • Fig. 4 is the side view of the first embodiment of the impeller of the present invention.
  • Figure 5 is a front view of the blade of the first embodiment of the impeller of the present invention (looking back from the front disc);
  • Figure 6 is a rear view of the blade of the first embodiment of the impeller of the present invention (looking forward from the rear disc);
  • Fig. 7 is the schematic diagram of the blade of the first embodiment of the impeller of the present invention.
  • Fig. 8 is the schematic diagram of the front disc of the first embodiment of the impeller of the present invention.
  • Fig. 9 is the enlarged schematic diagram of part I in Fig. 8.
  • FIG. 10 is a schematic diagram of the simulation diagram of the flow field trajectory in the impeller vane of the first embodiment of the impeller of the present invention.
  • Figure 11 is a side view of the second embodiment of the impeller of the present invention.
  • Figure 12 is a schematic diagram of the blade of the second embodiment of the impeller of the present invention.
  • Figure 13 is a side view of a third embodiment of the impeller of the present invention.
  • Fig. 14 is the schematic diagram of the blade of the third embodiment of the impeller of the present invention.
  • Figure 15 is a side view of a fourth embodiment of the impeller of the present invention.
  • Figure 16 is a schematic diagram of the blade of the fourth embodiment of the impeller of the present invention.
  • Figure 17 is a side view of the fifth embodiment of the impeller of the present invention.
  • Figure 18 is a schematic diagram of a blade of the fifth embodiment of the impeller of the present invention.
  • FIG. 19 is a schematic diagram of a simulation diagram of a flow field trajectory in a straight impeller blade channel in the prior art.
  • the range hood includes a fume collecting hood 400 and a fan system arranged in the fume collecting hood 400 , and the fan system is two horizontal centrifugal fans 100 arranged in parallel.
  • the centrifugal fan 100 can also be used in other types of range hoods, such as top suction type, side suction type, etc., or the fan system can also be a single fan system.
  • the centrifugal fan 100 includes a volute 300 and an impeller 200 disposed in the volute 300 .
  • the impeller 200 includes a front disc 1 , a rear disc 2 , blades 3 and a middle disc 4 disposed between the front disc 1 and the rear disc 2 .
  • the centrifugal fan 100 is a double inlet fan, the middle disk 4 is located between the front disk 1 and the rear disk 2 , and the blades 3 pass through the middle disk 4 .
  • inlet installation angle refers to the angle between the tangent of the leading edge of the blade and the tangent of the impeller circumference at this point.
  • the impeller 200 in the present invention has no pre-rotation effect in the centrifugal fan 100, the theoretically designed airflow enters the blade 3 to enter vertically, that is, the inlet installation angle is 90°, but the actual airflow enters the impeller 200 because the impeller The 200 rotation drives the surrounding airflow, so the nearby airflow has an inlet angle similar to pre-rotation.
  • the airflow enters the impeller in the axial direction, and the airflow changes from the axial direction to the radial flow.
  • the inlet installation angle of the blade 3 along the axial direction is less than 90 degrees.
  • the inlet installation angle of the blade 3 at the front disc 1, that is, the first inlet installation angle is ⁇ 1
  • the inlet installation angle of the blade 3 at the rear disc 2 that is, the second inlet installation angle is ⁇ 2 . Since the gas flow near the front disk 1 is smaller than the gas flow near the axial middle part (middle disk 4) and near the rear disk 2, therefore, in this embodiment, the first inlet installation angle is ⁇ 1 is smaller than the second inlet installation angle is ⁇ 2 .
  • the chord length of the blade 3 is also different, and the corresponding blade 3 has different functional capabilities.
  • the work force is weak, and the gas flow at the front plate 1 is small.
  • the structure matches the flow to reduce the unevenness of the outlet speed.
  • the inlet installation angle of the blade 3 gradually increases from front to rear in the axial direction.
  • the inlet installation angle of each position of the blade 3 in the axial direction is in the range of 65° to 87°.
  • the impeller 200 is close to the front disc 1, and has a lower working power.
  • a notch 31 is cut at the end where the blade 3 is connected to the front disc 1 to increase the outlet diameter of the current collector.
  • the notch 31 is formed by concave from the inlet to the outlet of each vane 3 .
  • the profile of the notch 31 includes a straight line segment A'B' and a curved line segment B'C' connected in sequence, the starting point A' of the straight line segment A'B' is close to the front plate 1, and the end point B' of the straight line segment A'B' and the curved line
  • the start point B' of the segment B'C' is the same, and the end point C' of the curve segment B'C' is far away from the front disc 1 .
  • Curve segment B'C' is preferably a logarithmic spiral segment.
  • the straight line segment A'B' is parallel to the airflow inlet velocity vector, and the curved segment B'C' is a smooth transition segment.
  • the logarithmic helix adopts a variable helix angle, and the variable helix angle increases or decreases gradually.
  • the range of the variable helix angle is -2 ° ⁇ 2°
  • the initial radius of the logarithmic spiral is 5mm.
  • the height of the entire blade 3 (dimension along the axial direction of the impeller 200 ) is b
  • the height of the notch 31 is b1
  • b1/b is preferably [1/16B, 3/16B], more preferably 1/8.
  • the impeller 200 forms a variable inner diameter structure.
  • the main work part of the impeller 200 is near the rear disc 2 and the middle disc 4 , and the work force is smaller at the front disc 1 .
  • the outer diameter of the impeller 200 is 250mm
  • the inner diameter of the impeller 200 is equal in the part of the blade 3 except for the notch 31, preferably 198mm, and the inner diameter of the impeller 200 is at most 215mm at the notch 31 of the blade 3.
  • variable inlet installation angle and variable inner diameter structure of the blade 3 above improve the unevenness of the outlet speed of the impeller 200 and help to improve the secondary vortex near the upper cover surface of the volute 300 .
  • the front end surface of the front disc 1 is designed with a curved surface, the radial inner side of the front disc 1 is radially outward, and its front end surface is gradually inclined toward the rear disc 2 .
  • the upper vertex (the inner end of the front disc 1) of the curved surface is flush with the upper cover surface of the volute 300 or slightly higher than the upper cover surface of the volute 300. The airflow backflow phenomenon caused by the hesitant gap between the impeller and the volute 300 can be effectively suppressed.
  • the profile of the curved surface is mainly designed with variable helix angle logarithmic helix and Bezier curve, including the first line segment AB, the second line segment BC and the third line segment CD which are smoothly connected in turn from the inside to the outside in the radial direction.
  • the first line segment AB is an arc-shaped transition segment.
  • the second line segment BC is a logarithmic spiral line segment with a variable helix angle.
  • the second line segment BC logarithmic helix adopts a variable helix angle, and the variable helix angle gradually increases or decreases.
  • the range of the variable helix angle is preferably -5° to 5°, and the initial radius of the logarithmic helix is preferably 15 mm.
  • the third line segment CD is a Bezier curve segment, including three segments Ce, ed, and dD, and is connected smoothly.
  • the blade 3 is designed as a slanted blade and constitutes a slanted impeller. Keep the blade inlet installation angle consistent with the inner diameter of the impeller (the inlet end of the blade 3 is parallel to the axis of the impeller 200), and change the blade chord length and outlet installation angle (the outlet end of the blade 3 is relatively inclined to the axis of the impeller 200).
  • ANSYS18.0 is used to simulate the flow field in the fan system of the range hood, and the airflow trace in the impeller channel is simulated by Fluent18.0 under the condition that the multi-blade centrifugal inclined impeller and the traditional straight impeller remain unchanged.
  • the figure is shown below. It can be seen from Figure 10 that the positive attack angle of the airflow in the blade passage of the multi-blade centrifugal inclined impeller is small, and there is only a small amount of flow separation area inside; while the positive attack angle of the airflow in the blade passage of the traditional straight impeller is obviously larger, and the flow inside the blade passage is large. There are many separate areas.
  • the outlet end 32 of the blade 3 forms a hypotenuse, and the hypotenuse is an inclined straight line, which is directly designed to linearly delay the wake vortex shedding in the axial direction, thereby improving the fluid flow inside the impeller.
  • the flow separation phenomenon in the impeller is significantly reduced.
  • the chord length of the blade 3 at the front disk 1 is L1
  • the chord length of the blade 3 at the rear disk 2 is L2
  • the chord length of the blade 3 gradually decreases from the front disk 1 to the rear disk 2 along the axial direction of the impeller, and satisfies L1: L2 ⁇ [15: 14, 5: 2]
  • the outer diameter of the impeller is D2
  • the inner diameter of the impeller is D1, D1: D2 ⁇ [0.78, 0.88].
  • D1 is taken from the place where there is no gap 31 in the blade 3 . If the inclination angle of the hypotenuse of blade 3 is too large, the efficiency of the fan system will be affected, and the overall efficiency of the fan system will be reduced. If the inclination angle is too small, the overall performance will change little. The performance can also effectively reduce noise.
  • the second embodiment of the impeller of the present invention As shown in Figure 11 and Figure 12, it is the second embodiment of the impeller of the present invention.
  • the difference between the impeller of this embodiment and the above-mentioned first embodiment is that the chord length of the blade 3 increases gradually from the front disk 1 to the middle disk 4 along the axial direction of the impeller 200 , and then gradually decreases from the middle disk 4 to the rear disk 2 Small.
  • the outlet ends of the blades 3 are both oblique edges between the front disc 1 and the middle disc 4 and between the middle disc 4 and the rear disc 2 .
  • the above-mentioned blades 3 still have the effect of reducing the flow separation of the airflow in the impeller channel, thereby reducing noise, and the structure of the blades 3 is simple to install.
  • the chord length of blade 3 at the position corresponding to mid-disk 4 is L3, and satisfies L3: L1 ⁇ [15:14, 5:2], L3: L2 ⁇ [15:14, 5:2], D1: D2 ⁇ [ 0.78, 0.88].
  • the height of the vane 3 between the front disc 1 and the middle disc 4 and the height of the vane 3 between the middle disc 4 and the rear disc 2 can be given according to the fluid motion law in the impeller 200 and the actual demand.
  • the outlet end of the blade 3 is curved between the front disk 1 and the middle disk 4 and between the middle disk 4 and the rear disk 2, and the curve moves according to the fluid movement.
  • the law can be a Bezier curve or an Archimedes spiral. According to the actual fluid flow requirements, determine the two points of the front and rear discs, and fit the curve for the highest point of the blade in the place where the fluid is most unobstructed. Since this type of blade 3 can better fit the law of fluid motion along the axial direction, the blade 3 phase has a better effect in reducing the flow separation of the airflow in the blade passage of the impeller 200, thereby reducing noise.
  • the centrifugal fan 100 is a single-inlet fan, that is, the impeller 200 is not provided with the middle disk 4, and the form of the blades 3 remains unchanged, which can still reduce the flow separation of the airflow in the impeller channel. Thereby reducing the noise.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

一种叶轮（200），包括前盘(1)、后盘(2)以及设置在前盘(1)和后盘(2)之间的叶片(3)，叶片(3)的进口安装角沿叶轮（200）轴向由前盘(1)向后盘(2)逐渐增大。还公开了一种应用有上述叶轮（200）的离心风机（100），以及应用有上述离心风机（100）的吸油烟机。与现有技术相比，通过设置沿轴向渐变的进口安装角，使得做功能力匹配气体流量，从而改善叶轮（200）出口速度的不均匀性，能够改善蜗壳（300）上盖面附近的二次涡流。

Description

一种叶轮、应用有该叶轮的离心风机和吸油烟机 技术领域
本发明涉及油烟净化装置的技术领域，尤其涉及一种叶轮和应用有该叶轮的离心风机，也涉及一种应用有该离心风机的吸油烟机。
背景技术
吸油烟机已成为现代家庭中不可或缺的厨房家电设备之一。吸油烟机是利用流体动力学原理进行工作，通过安装在吸油烟机内部的离心式风机吸排油烟，并使用滤网过滤部分油脂颗粒。离心式风机包括蜗壳、安装在蜗壳中叶轮及带动叶轮转动的电机。当叶轮旋转时，在风机中心产生负压吸力，将吸油烟机下方的油烟吸入风机，经过风机加速后被蜗壳收集、引导排出室外。
针对吸油烟机薄型机，风机系统一般采用水平放置，出风口以顶出风为主。如中国专利CN207006315U(专利号为201720917014.9)公开的一种超薄型顶吸式吸油烟机，至少包括壳体和送风结构件，送风结构件包括风机蜗壳、与风机蜗壳配合使用的电机和风轮，风机蜗壳包括设有进风口的前盖板和中间环壁，中间环壁以连续平滑过渡的曲面将所述前盖板垂直连接起来并形成一个具有上开口的内流道和送风口。
在该种情况下，风机系统的进风口和出风口在同一方向上，造成流体在风机系统中进入蜗壳有90度的转弯，在蜗壳内经过离心叶轮的离心甩吸净化后，尚需转90度弯后才能经过出风口排出。流体在较高速度下经过两次的90度转弯，对流体的噪音和能量损失较大，造成整机性能在同一风量下，噪音明显偏高。
因此市场上出现采用轴流叶轮和混流叶轮，这两款叶轮相对比较适用于卧式风机系统的吸油烟机中。根据卧式并联双风机系统式的吸油烟机，采用轴流叶轮或者混流叶轮更符合流体运动规律，但是目前市场上的轴流叶轮、混流叶轮和离心叶轮等叶轮，轴流叶轮和混流叶轮本身具有噪音高的特点，因此，在家用吸油烟机中，整机性能测试中，噪音仍然明显偏高；多翼离心叶轮(即西罗柯型叶轮，特点为直径比大，相对宽度大，叶片数多的前向叶轮，但是效率低)是唯一一个具有噪音低的特点。因此，虽然轴流叶轮、混流叶轮相对更适合该吸油烟机的流场运动规律，但是由于叶轮本身噪音较高，通过试验对比，同一风量下仍然是多翼离心叶轮的噪音低。
吸油烟机上绝大多数多翼离心叶轮的形态，由叶轮前后端盘、叶片和轮盘等组成。这种类型的叶轮的叶片在高度方向上叶片弦长相等。由于叶轮前盘为平面结构，考虑到叶轮动平衡性，叶轮前盖盘与蜗壳之间有一定的距离，在该处易发生回流现象。再者，由于流体由集流器沿轴向进入叶轮内，而且多翼离心叶轮的相对宽度较大，在叶轮轴向 方向上，风机叶轮叶片进口处气流整体向盘侧倾斜。叶轮出口气流受到进气情况影响，沿轴向呈不均匀分布，造成前向风机蜗壳内二次涡流。参见图18，气流通过集流器进入叶轮内，形成较大的正冲角，而且同一叶轮在小流量下运转时会产生比大流量工况下更大的正冲角，由于轴向气流呈不均匀分布，叶道靠近上盖盘处流量偏小，正冲角更大，叶道内流动分离现象更明显，流动分离现象明显造成噪音大。
发明内容
本发明所要解决的第一个技术问题是针对上述现有技术存在的不足，提供一种叶轮，能够降低噪音。
本发明所要解决的第二个技术问题是提供一种应用有上述叶轮的离心风机。
本发明所要解决的第三个技术问题是提供一种应用有上述离心风机的吸油烟机。
本发明解决上述第一个技术问题所采用的技术方案为：一种叶轮，包括前盘、后盘以及设置在前盘和后盘之间的叶片，其特征在于：所述叶片的进口安装角沿叶轮轴向由前盘向后盘逐渐增大。
优选地，所述叶片沿轴向各位置的进口安装角的大小在65°～87°范围之间。
所述叶片在前盘处的弦长为L1，所述叶片在后盘处的弦长为L2，所述叶片的弦长沿叶轮轴向从前盘向后盘逐渐减小，所述叶轮外径为D2，所述叶轮内径为D1，并且满足L1：L2∈[15：14，5：2]、D1：D2∈[0.78，0.88]。
根据本发明的一个方面，所述叶轮还包括位于前盘和后盘之间的中盘，所述叶片穿过中盘，所述叶片在前盘处的弦长为L1，所述叶片在后盘处的弦长为L2，所述叶片在中盘处的弦长为L3，所述叶片的弦长沿叶轮轴向从前盘向中盘逐渐增大、从中盘向后盘逐渐减小，所述叶轮外径为D2，所述叶轮内径为D1，并且满足L3：L1∈[15：14，5：2]、L3：L2∈[15：14，5：2]、D1：D2∈[0.78，0.88]。
根据本发明的另一个方面，所述叶片具有出口端，所述叶片的出口端在前盘和中盘之间、在中盘和后盘之间均为直线；或者所述叶片的出口端在前盘和中盘之间、在中盘和后盘之间均为曲线，所述曲线为贝塞尔曲线或阿基米德螺旋线。
根据本发明的另一个方面，所述叶片在前盘处的弦长为L1，所述叶片在后盘处的弦长为L2，所述叶片的弦长沿叶轮轴向从前盘向后盘逐渐增大，所述叶轮外径为D2，所述叶轮内径为D1，并且满足L1：L2∈[2：5，14：15]、D1：D2∈[0.78，0.88]。
为进一步改善叶片出口速度的不均匀性，所述叶片与前盘连接的一端开设有缺口，所述缺口从每个叶片的进口向出口方向凹陷而形成，所述叶片整体的高度为b，所述缺 口的高度为b1，并且满足b1/b∈[1/16B，3/16B]。
优选地，所述缺口的型线包括依次连接的直线段和曲线段，所述直线段的起点靠近前盘，所述直线段的终点和曲线段的起点相同，所述曲线段的终点远离前盘，所述曲线段为光滑过渡段。
为便于当叶轮安装在离心风机中时，优化前盘和蜗壳之间间隙处的气流回流现象，提高离心风机工作效率，所述前盘的前端面采用曲面设计，所述前盘的前端面从径向内侧向径向外侧逐渐向后盘方向倾斜，所述倾斜的前端面为朝向叶轮内凹陷的曲线。
优选地，所述曲面的型线包括在径向上由内向外依次光滑连接的第一线段、第二线和第三线段，所述第一线段为圆弧形的过渡段，所述第二线段为变螺旋角对数螺旋线段，所述第三线段为贝塞尔曲线段。
本发明解决上述第二个技术问题所采用的技术方案为：一种离心风机，其特征在于：应用有如上所述的叶轮。
本发明解决上述第三个技术问题所采用的技术方案为：一种吸油烟机，其特征在于：应用有如上所述的离心风机。
与现有技术相比，本发明的优点在于：通过设置沿轴向渐变的进口安装角，使得做功能力匹配气体流量，从而改善叶轮出口速度的不均匀性，应用于风机中时，能够改善蜗壳上盖面附近的二次涡流；通过使得叶片在前盘处形成缺口，形成变内径结构，能够进一步改善叶轮出口速度的不均匀性，还能够拓宽叶道，增大进气量；前盘的前端面采用曲面设计，应用于风机中时，能够优化前盘与蜗壳之间间隙处的气流回流现象，提高风机系统工作效率；叶轮为斜叶轮，能够减小叶道内的流动分离区域，减弱流动分离程度，从而降低流体噪音。
附图说明
图1为本发明的吸油烟机实施例的结构示意图；
图2为本发明的吸油烟机实施例的剖视图；
图3为本发明的叶轮第一个实施例的结构示意图；
图4为本发明的叶轮第一个实施例的侧视图；
图5为本发明的叶轮第一个实施例的叶片的前视图(由前盘向后看)；
图6为本发明的叶轮第一个实施例的叶片的后视图(由后盘向前看)；
图7为本发明的叶轮第一个实施例的叶片的示意图；
图8为本发明的叶轮第一个实施例的前盘的示意图；
图9为图8中局部Ⅰ的放大示意图；
图10为本发明叶轮的第一个实施例的叶轮叶道内流场轨迹仿真示意图。
图11为本发明的叶轮第二个实施例的侧视图；
图12为本发明的叶轮第二个实施例的叶片的示意图；
图13为本发明的叶轮第三个实施例的侧视图；
图14为本发明的叶轮第三个实施例的叶片的示意图；
图15为本发明的叶轮第四个实施例的侧视图；
图16为本发明的叶轮第四个实施例的叶片的示意图；
图17为本发明的叶轮第五个实施例的侧视图；
图18为本发明的叶轮第五个实施例的叶片的示意图；
图19为现有技术的直叶轮叶道内流场轨迹仿真示意图。
具体实施方式
下面详细描述本发明的实施例，所述实施例的示例在附图中示出，其中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。
在本发明的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“长度”、“宽度”、“厚度”、“上”、“下”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”“内”、“外”、“顺时针”、“逆时针”、“轴向”、“径向”、“周向”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发明和简化描述，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，由于本发明所公开的实施例可以按照不同的方向设置，所以这些表示方向的术语只是作为说明而不应视作为限制，比如“上”、“下”并不一定被限定为与重力方向相反或一致的方向。此外，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。
如图1和图2所示，为本发明的一种吸油烟机的一个优选实施例，本实施例中为薄型吸油烟机。该吸油烟机包括集烟罩400和设置在集烟罩400内的风机系统，风机系统为两个卧式并联布置的离心风机100。可替代的，该离心风机100也可以用于其他形式的吸油烟机，如顶吸式、侧吸式等，或者风机系统也可以为单风机系统。
离心风机100包括蜗壳300和设置在蜗壳300内的叶轮200。
叶轮实施例一
如图3和图4所示，为本发明叶轮的实施例一。该叶轮200包括前盘1、后盘2、设置在前盘1和后盘2之间的叶片3和中盘4。叶片3具有至少两个，沿着前盘1(或后盘2)的周向间隔布置。本实施例中，叶片3的数量在60个左右。
离心风机100为双进风风机，中盘4位于前盘1和后盘2之间，叶片3穿过中盘4。
下文所述的“进口安装角”是指：叶片前缘点的切线与该点叶轮圆周切线之间的夹角。
参见图5和图6，由于本发明中叶轮200在离心风机100中无预旋作用，理论设计 气流进入叶片3为垂直进入，即进口安装角为90°，但是实际气流进入叶轮200前由于叶轮200旋转带动周围气流运动，所以附近气流有一个类似预旋的入口角度，气流沿轴向进入叶轮，气流由轴向转为径向流动，叶片3沿轴向的进口安装角小于90度。在前盘1处叶片3的进口安装角，即第一进口安装角为β 1，在后盘2处叶片3的进口安装角，即第二进口安装角为β 2。由于靠近前盘1的气体流量小于轴向中间部分(中盘4)和靠近后盘2的气体流量，因此，本实施例中，第一进口安装角为β 1小于第二进口安装角为β 2。进口安装角不同的情况下，叶片3的弦长也不同，对应的叶片3做功能力不同，即在前盘1处第一进口安装角为β 1较小，叶片3的弦长较短，做功能力偏弱，而前盘1处气体流量少，该结构和该流量匹配，减少出口速度的不均匀性。叶片3沿轴向由前向后进口安装角逐渐增大，优选的，叶片3沿轴向各位置的进口安装角的范围在65°～87°范围之间。
参见图3和图7，叶轮200在靠近前盘1处，做功能力较小，为了拓宽流道，在叶片3与前盘1连接的一端切缺口31而增大集流器的出口直径从而增大进气流量，该缺口31从每个叶片3的进口向出口方向凹陷而形成。缺口31的型线包括依次连接的直线段A’B’和曲线段B’C’，直线段A’B’的起点A’靠近前盘1，直线段A’B’的终点B’和曲线段B’C’的起点B’相同，曲线段B’C’的终点C’远离前盘1。曲线段B’C’优选的为对数螺旋线段。直线段A’B’平行于气流入口速度矢量，曲线段B’C’为光滑过渡段，对数螺旋线采用变螺旋角，变螺旋角渐增或者渐缩，变螺旋角的范围为-2°～2°，对数螺旋线的初始半径为5mm。叶片3整体的高度(沿叶轮200轴向的尺寸)为b，缺口31的高度为b1，b1/b优选的[1/16B，3/16B]，更为优选的为1/8。
由此，叶轮200形成变内径结构。叶轮200的主要做功部分在后盘2和中盘4附近，而在前盘1处做功能力较小。叶轮200的外径为250mm，叶轮200的内径在叶片3除缺口31外的部分为等径，优选的为198mm，叶轮200的内径在叶片3的缺口31处最大为215mm。
上述叶片3的变进口安装角和变内径结构，改善了叶轮200出口速度的不均匀性，有助于改善蜗壳300上盖面附近的二次涡流。
参见图4、图8和图9，为了优化前盘1和蜗壳300之间间隙处的气流汇流现象，提高离心风机工作效率。前盘1的前端面采用曲面设计，前盘1的径向内侧向径向外侧、其前端面逐渐向后盘2方向倾斜，该倾斜面为朝向叶轮200内凹陷的曲线。该曲面在离心风机装配中上顶点(前盘1内侧端部)和蜗壳300上盖面齐平或者稍微高于蜗壳300上盖面，和集流器搭配使用，吻合进口流体运动规律，可以有效的抑制叶轮和蜗壳300之间犹豫间隙原因引起的气流回流现象。
曲面的型线主要采用变螺旋角对数螺旋线和贝塞尔曲线设计，包括在径向上由内向外依次光滑连接的第一线段AB、第二线段BC和第三线段CD。其中第一线段AB为圆 弧形的过渡段。第二线段BC为变螺旋角对数螺旋线段，在有限蜗壳300高度的空间内增加叶轮200的有效高度，提高做功能力，增加风量，抑制回流，降低噪音，优化前盘1与蜗壳300之间间隙处的气流回流现象，提高风机系统工作效率。第二线段BC对数螺旋线采用变螺旋角，变螺旋角渐增或者渐缩，变螺旋角的范围优选的为-5°～5°，对数螺旋线的初始半径优选的为15mm。第三线段CD为贝塞尔曲线段，包括Ce、ed、dD三段，并且光滑连接，优选的，贝塞尔曲线优选的满足方程B(t)＝C·(1-t) 3+3·e·t·(1-t) 2+3·d·(1-t)·t 2+D·t 3，其中t∈[0，1]，C，e，d，D分别为四点坐标(坐标系以点D为原点，叶轮200径向为X轴，叶轮200轴向为Y轴)。
为了减小叶道内的流动分离区域，减弱流动分离程度，从而降低流体噪音。参见图7，叶片3为斜叶片设计，构成斜叶轮。保持叶片进口安装角和叶轮内径一致(叶片3的进口端与叶轮200的轴线平行)，更改叶片弦长和出口安装角(叶片3的出口端与叶轮200的轴线相对倾斜)。采用ANSYS18.0对吸油烟机风机系统内流场进行流体仿真，分别采用多翼离心斜叶轮和传统直叶轮其他结构保持不变的情况下，通过Fluent18.0仿真出叶轮叶道内的气流迹线图如下图所示。由图10可知，多翼离心斜叶轮在叶道内气流的正冲角较小，内部只有少量有流动分离的区域；而传统直叶轮在叶道内气流的正冲角明显偏大，叶道内部流动分离的区域较多。由此可知，通过改进叶轮叶片的形态改善了叶轮叶道内的流动分离现象，不仅提高了风机系统的工作效率，而且降低了风机系统的噪声。在整机试验测试中，采用方太半消音室测试整机的噪音，仅更换叶轮测试发现，多翼离心斜叶轮的噪音低于传统多翼离心直叶轮1.5dB。
叶片3的出口端32构成斜边，斜边为倾斜直线，直接设计为沿轴向按照线性延缓尾迹涡脱落，从而改善叶轮内部流体流动，相比较传统叶轮，叶轮内气流流动分离现象明显减少。
叶片3在前盘1处的弦长为L1，叶片3在后盘2处的弦长为L2，叶片3的弦长沿叶轮轴向从前盘1向后盘2逐渐减小，并且满足L1：L2∈[15：14，5：2]，叶轮外径为D2，叶轮内径为D1，D1：D2∈[0.78，0.88]。此处D1取叶片3无缺口31处。如果叶片3斜边倾斜角度太大的话会影响风机系统的效率，风机系统整机效率降低，而倾斜角度太小，整体性能改变较小，在上述范围内，即能保证风机系统在整机上的性能也可以有效降低噪音。
叶轮实施例二
如图11和图12所示，为本发明叶轮的实施例二。本实施例的叶轮，与上述实施例一的不同之处在于，叶片3的弦长沿叶轮200的轴向由前盘1到中盘4逐渐增大、再从中盘4到后盘2逐渐减小。叶片3的出口端在前盘1和中盘4之间、在中盘4和后盘2 之间均为斜边。上述叶片3仍有降低叶轮叶道内气流流动分离，从而降低噪音的作用，并且这种叶片3结构安装简单。
叶片3在与中盘4对应处的弦长为L3，并且满足L3：L1∈[15：14，5：2]，L3：L2∈[15：14，5：2]，D1：D2∈[0.78，0.88]。叶片3在前盘1和中盘4之间的高度、叶片3在中盘4和后盘2之间的高度可以根据叶轮200内流体运动规律和实际需求给定。
叶轮实施例三
如图13和图14所示，为本发明叶轮的实施例三。本实施例的叶轮与上述实施例二的不同之处在于，叶片3的出口端在前盘1和中盘4之间、在中盘4和后盘2之间均为曲线，曲线按照流体运动规律，可以采用贝塞尔曲线或阿基米德螺旋线。根据实际流体流动的需求，确定前后盘的两点，在流体最通畅的地方为叶片最高点拟合曲线。由于该类型的叶片3能更好的拟合沿轴向流体运动的规律，所以该叶片3相在降低叶轮200叶道内的气流流动分离有较好的效果，从而降低噪音。
叶轮实施例四
如图15和图16所示，为本发明叶轮的实施例四。本实施例的叶轮与实施例一的不同之处在于，叶片3的出口端的倾斜方向与实施例一相反，即叶片3的弦长从前盘1向后盘2逐渐增大，L1：L2∈[2：5，14：15]，D1：D2∈[0.78，0.88]。
叶轮实施例五
如图17和图18所示，为本发明叶轮的实施例五。本实施例的叶轮与实施例一的不同之处在于，离心风机100为单进风风机，即叶轮200不设置中盘4，叶片3形式保持不变，仍能够降低叶轮叶道内气流流动分离，从而起到降低噪音的作用。

Claims (12)

  1. 一种叶轮，包括前盘(1)、后盘(2)以及设置在前盘(1)和后盘(2)之间的叶片(3)，其特征在于：所述叶片(3)的进口安装角沿叶轮轴向由前盘(1)向后盘(2)逐渐增大。
  2. 根据权利要求1所述的叶轮，其特征在于：所述叶片(3)沿轴向各位置的进口安装角的大小在65°～87°范围之间。
  3. 根据权利要求1所述的叶轮，其特征在于：所述叶片(3)在前盘(1)处的弦长为L1，所述叶片(3)在后盘(2)处的弦长为L2，所述叶片(3)的弦长沿叶轮轴向从前盘(1)向后盘(2)逐渐减小，所述叶轮外径为D2，所述叶轮内径为D1，并且满足L1∶L2∈[15∶14，5∶2]、D1∶D2∈[0.78，0.88]。
  4. 根据权利要求1所述的叶轮，其特征在于：所述叶轮还包括位于前盘(1)和后盘(2)之间的中盘(4)，所述叶片(3)穿过中盘(4)，所述叶片(3)在前盘(1)处的弦长为L1，所述叶片(3)在后盘(2)处的弦长为L2，所述叶片(3)在中盘(4)处的弦长为L3，所述叶片(3)的弦长沿叶轮轴向从前盘(1)向中盘(4)逐渐增大、从中盘(4)向后盘(2)逐渐减小，所述叶轮外径为D2，所述叶轮内径为D1，并且满足L3∶L1∈[15∶14，5∶2]、L3∶L2∈[15∶14，5∶2]、D1∶D2∈[0.78，0.88]。
  5. 根据权利要求4所述的叶轮，其特征在于：所述叶片(3)具有出口端(32)，所述叶片(3)的出口端(32)在前盘(1)和中盘(4)之间、在中盘(4)和后盘(2)之间均为直线；或者所述叶片(3)的出口端(32)在前盘(1)和中盘(4)之间、在中盘(4)和后盘(2)之间均为曲线，所述曲线为贝塞尔曲线或阿基米德螺旋线。
  6. 根据权利要求1所述的叶轮，其特征在于：所述叶片(3)在前盘(1)处的弦长为L1，所述叶片(3)在后盘(2)处的弦长为L2，所述叶片(3)的弦长沿叶轮轴向从前盘(1)向后盘(2)逐渐增大，所述叶轮外径为D2，所述叶轮内径为D1，并且满足L1∶L2∈[2∶5，14∶15]、D1∶D2∈[0.78，0.88]。
  7. 根据权利要求1～6中任一项所述的叶轮，其特征在于：所述叶片(3)与前盘(1)连接的一端开设有缺口(31)，所述缺口(31)从每个叶片(3)的进口向出口方向凹陷而形成，所述叶片(3)整体的高度为b，所述缺口(31)的高度为b1，并且满足b1/b∈[1/16B，3/16B]。
  8. 根据权利要求7所述的叶轮，其特征在于：所述缺口(31)的型线包括依次连接的直线段(A’B’)和曲线段(B’C’)，所述直线段(A’B’)的起点(A’)靠近前盘(1)，所述直线段(A’B’)的终点(B’)和曲线段(B’C’)的起点(B’)相同，所述曲线段(B’C’)的终点(C’)远离前盘(1)，所述曲线段(B’C’)为光滑过渡段。
  9. 根据权利要求1～6中任一项所述的叶轮，其特征在于：所述前盘(1)的前端面采用曲面设计，所述前盘(1)的前端面从径向内侧向径向外侧逐渐向后盘(2)方向倾斜，所述倾斜的前端面为朝向叶轮内凹陷的曲线。
  10. 根据权利要求9所述的叶轮，其特征在于：所述曲面的型线包括在径向上由内向外依次光滑连接的第一线段(AB)、第二线段(BC)和第三线段(CD)，所述第一线段(AB)为圆弧形的过渡段，所述第二线段(BC)为变螺旋角对数螺旋线段，所述第三线段(CD)为贝塞尔曲线段。
  11. 一种离心风机，其特征在于：应用有如权利要求1～10中任一项所述的叶轮。
  12. 一种吸油烟机，其特征在于：应用有如权利要求10所述的离心风机。
PCT/CN2020/124782 2020-10-13 2020-10-29 一种叶轮、应用有该叶轮的离心风机和吸油烟机 WO2022077585A1 (zh)

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