WO2022062130A1 - 离心风轮和具有其的空气处理设备 - Google Patents

离心风轮和具有其的空气处理设备 Download PDF

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Publication number
WO2022062130A1
WO2022062130A1 PCT/CN2020/128977 CN2020128977W WO2022062130A1 WO 2022062130 A1 WO2022062130 A1 WO 2022062130A1 CN 2020128977 W CN2020128977 W CN 2020128977W WO 2022062130 A1 WO2022062130 A1 WO 2022062130A1
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WIPO (PCT)
Prior art keywords
hub
air inlet
wind wheel
end point
centrifugal
Prior art date
Application number
PCT/CN2020/128977
Other languages
English (en)
French (fr)
Inventor
付裕
Original Assignee
广东美的制冷设备有限公司
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 CN202022179591.7U external-priority patent/CN212744474U/zh
Priority claimed from CN202011044953.XA external-priority patent/CN112049816A/zh
Application filed by 广东美的制冷设备有限公司 filed Critical 广东美的制冷设备有限公司
Priority to EP20954974.0A priority Critical patent/EP4166792A4/en
Publication of WO2022062130A1 publication Critical patent/WO2022062130A1/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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/08—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation
    • F04D25/082—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation the unit having provision for cooling the motor
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/5806—Cooling the drive system
    • 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
    • F04D17/162—Double suction pumps

Definitions

  • the present application relates to the technical field of air treatment devices, and in particular, to a centrifugal fan wheel and air treatment equipment having the same.
  • the centrifugal wind wheel rotates by the input of mechanical energy, thereby increasing the gas pressure and realizing the gas discharge.
  • the air volume of the centrifugal wind wheel is low, and the ventilation efficiency is low.
  • the present application aims to solve at least one of the technical problems existing in the related art. To this end, the present application proposes a centrifugal wind wheel, the centrifugal wind wheel has large ventilation air volume and ventilation efficiency, and has good sound quality.
  • the present application also proposes an air treatment device having the above centrifugal fan.
  • the centrifugal wind wheel includes: a hub, a plurality of air inlet holes are formed on the hub, and the plurality of air inlet holes are arranged at intervals along the circumferential direction of the hub, each of the The air inlet holes pass through the hub; the blades are multiple, and the multiple blades are all arranged on the hub, and the multiple blades are arranged at intervals along the circumferential direction of the hub and are arranged at intervals on the multiple On the radially outer side of the air inlet holes, the number of the blades is equal to the number of the air inlet holes, and each of the blades and the corresponding air inlet holes are arranged opposite to the radial direction of the hub.
  • the centrifugal wind wheel of the embodiment of the present application by forming a plurality of air inlet holes on the hub, and making the number of air inlet holes equal to the number of blades, and each air inlet hole and the corresponding blade are arranged opposite to the radial direction of the hub, while ensuring the structural strength of the centrifugal wind wheel, the ventilation air volume and ventilation efficiency of the centrifugal wind wheel are effectively improved, and the flow field of the centrifugal wind wheel is guaranteed to be stable, so that the centrifugal wind wheel has good sound quality.
  • the air inlet hole extends radially of the hub and has a profile extending radially of the hub, and the blade has a bone line extending radially of the hub, at On the cross section of the hub, the orthographic projection of the central axis of the hub, the radially outer end point of the orthographic projection of the profile line and the radially inner end point corresponding to the orthographic projection of the bone line are located on the same straight line.
  • the profile line is formed as a straight line, and on the cross section of the hub, the orthographic projection of the central axis of the wheel hub, the radially outer end point of the orthographic projection of the profile line, the positive side of the profile line.
  • the radially medial end point of the projection and the radially medial end point of the orthographic projection corresponding to the bone line are located on the same line.
  • the radial inner end point of the orthographic projection of the bone line corresponds to the end points on both sides of the orthographic projection of the outer contour of the air inlet hole in the circumferential direction of the hub They are respectively connected into a first straight line and a second straight line.
  • the angle formed between the first straight line and the second straight line toward the corresponding air inlet hole is ⁇ , and the ⁇ satisfies: 120° ⁇ ⁇ 135°.
  • the distance between the radial inner end point of the profile line and the center axis of the hub is L 0 , and the L 0 satisfies: L 0 ⁇ 0.3R, wherein , R is the radius of the centrifugal wind wheel.
  • the length of the profile line is L 1 , and the L 1 satisfies: 0.3L ⁇ L 1 ⁇ 0.2R, where L is the blade at the hub The length in the radial direction, R is the radius of the centrifugal wind wheel.
  • the distance between the radially outer end point of the profile line and the radially inner end point corresponding to the bone line is L 2
  • the L 2 satisfies: 1mm ⁇ L 2 ⁇ 0.3L
  • L is the length of the blade in the radial direction of the hub.
  • the centrifugal rotor further includes: a reinforcing ring, the reinforcing ring and the hub are arranged at intervals along the axial direction of the hub, and are respectively located at both ends of the length of the blade.
  • the air treatment equipment according to the embodiment of the second aspect of the present application includes the centrifugal fan according to the embodiment of the first aspect of the present application.
  • the air treatment equipment of the embodiments of the present application by using the above-mentioned centrifugal fan, the air volume of the air treatment equipment is effectively improved, and the sound quality of the air treatment equipment is ensured at the same time.
  • the air treatment equipment is an air conditioner and has a fresh air duct, and the centrifugal wind wheel is arranged in the fresh air duct.
  • FIG. 1 is a schematic diagram of a centrifugal wind wheel according to an embodiment of the present application.
  • Fig. 2 is the enlarged view of A part circled in Fig. 1;
  • Fig. 3 is another schematic diagram of the centrifugal wind wheel shown in Fig. 1;
  • Fig. 4 is another schematic diagram of the centrifugal wind wheel described in Fig. 3;
  • Figure 5 is an enlarged view of the B part circled in Figure 4.
  • FIG. 6 is a schematic diagram of airflow flow of a centrifugal wind wheel in the related art.
  • centrifugal impeller 100 according to the embodiment of the first aspect of the present application will be described with reference to the accompanying drawings.
  • the centrifugal wind wheel 100 includes a hub 1 and blades 2 .
  • the hub 1 is formed with a plurality of air inlet holes 10 , and the plurality of air inlet holes 10 are arranged at intervals along the circumference of the hub 1 .
  • the air duct 20 is communicated with the air inlet holes 10 , and the plurality of blades 2 are arranged radially outside the plurality of air inlet holes 10 at intervals, then in the radial direction of the hub 1 , the plurality of air inlet holes 10 are located on the inner side of the plurality of blades 2 .
  • the centrifugal wind wheel 100 rotates, a part of the airflow flows to the inside of the plurality of blades 2 through the air inlet holes 10, and another part of the airflow flows to the inside of the multiple blades 2 through the end of the blade 2 away from the hub 1, and both parts of the airflow pass through the centrifugal
  • the air duct 20 flows out, thereby increasing the air intake area of the centrifugal wind wheel 100, effectively improving the ventilation air volume of the centrifugal wind wheel 100, thereby improving the ventilation efficiency of the centrifugal wind wheel 100, and the hub 1 is suitable for being connected with the motor,
  • the airflow flowing to the inner side of the blade 2 through the air inlet hole 10 can also effectively dissipate heat to the motor, so as to cool the motor.
  • "plurality" means two or more.
  • the number of blades 2 is equal to the number of air inlet holes 10 , then each blade 2 corresponds to one air inlet hole 10 respectively, and each air inlet hole 10 corresponds to one blade 2 respectively, so that The plurality of air inlet holes 10 and the plurality of blades 2 are respectively arranged in a one-to-one correspondence; each blade 2 and the corresponding air inlet hole 10 are arranged opposite to each other in the radial direction of the hub 1, then in the radial direction of the hub 1, each blade 2 is respectively arranged.
  • the air flow out of the air inlet hole 10 can flow into the centrifugal air duct 20 more smoothly for acceleration, so as to avoid the flow field of the centrifugal wind wheel 100 due to
  • the setting of the air inlet hole 10 is unstable and causes abnormal sound, thereby ensuring the stability of the flow field of the centrifugal wind wheel 100, thereby ensuring that no other abnormal sound is generated during the rotation of the centrifugal wind wheel 100, so that the centrifugal wind wheel 100 has a good performance. Sound quality to ensure user experience.
  • outside direction refers to the direction away from the center axis 1a of the hub 1 in the radial direction of the hub 1, and the opposite direction is defined as “inside”.
  • the centrifugal impeller 100 of the embodiment of the present application by forming a plurality of air inlet holes 10 on the hub 1 , the number of the air inlet holes 10 is equal to the number of the blades 2 , and each air inlet hole 10 is along the corresponding blade 2 .
  • the radially opposite arrangement of the hub 1 not only ensures the structural strength of the centrifugal wind wheel 100, but also effectively improves the ventilation air volume and ventilation efficiency of the centrifugal wind wheel 100.
  • Wheel 100 has good sound quality. Therefore, the present application can improve the ventilation efficiency and stability of the centrifugal wind wheel 100 without changing the overall structural size of the centrifugal wind wheel 100 , so that the centrifugal wind wheel 100 has good applicability and practicability.
  • the inventors of the present application compared the centrifugal wind rotor 100 of the embodiment of the present application with the centrifugal wind rotor without air inlet holes in the related art, and the results obtained that, under the same rotational speed, the centrifugal wind rotor 100 in the present application compared
  • the air volume of the centrifugal wind wheel in the related art has been significantly improved, and the air volume can be increased by 10%, and it has been verified that the centrifugal wind wheel 100 of the present application does not produce abnormal sound during operation, and the frequency spectrum and hearing are not abnormal. And meet the drop requirements, no safety hazards, with good reliability.
  • openings are arranged on the contour of the centrifugal wind wheel, and the arrangement of the openings is unfounded and relatively arbitrary. There are 6 openings, so that the air volume of the centrifugal wind wheel is limited.
  • the number of air inlet holes 10 is set equal to the number of blades 2, and each air inlet hole 10 and the corresponding blade 2 are arranged radially opposite to each other along the hub 1, so as to ensure the structural strength of the centrifugal wind wheel 100, and further The air volume is increased, the flow field of the centrifugal wind wheel 100 is stabilized, and other abnormal noises are prevented from being generated by the centrifugal wind wheel 100 .
  • FIG. 6 shows the difference in the flow state of a centrifugal impeller with six openings in the hub opening in some technologies.
  • a centrifugal wind rotor with 6 openings because the openings are too large, if the area formed by the adjacent blades is regarded as an air duct, the difference in the flow direction of the gas flowing into a single air duct will be too large.
  • the airflow deflection angle ⁇ 2- ⁇ 1 in the entire air duct (where ⁇ 2 is the airflow outlet angle, and ⁇ 1 is the airflow inlet angle) is often around 75°. Such a large airflow change will cause the flow loss of the airflow with a large difference in the flow direction to be more obvious.
  • the energy of the air flow introduced by the large openings will be offset, so that the air volume cannot be effectively increased; and the air flow flowing into the air inlet hole 10 in this application can gradually flow in the direction of the profile line ⁇ 1 of the blade 2. Due to the Coanda effect of the fluid, The flow state is more stable, the flow loss is smaller, and the work efficiency of a single blade 2 is higher, thereby bringing a larger air volume.
  • the centrifugal wind rotor will receive a pulling force of about 3000 times its own mass.
  • the solution of 6 openings in the above technology is even more untenable, because the blade strength is far from meeting the requirements of high-speed operation.
  • the number of air inlet holes 10 and the number of blades 2 is 1:1, and the structural strength of the centrifugal wind rotor 100 has been verified by experiments to fully meet the requirements.
  • the hub 1 includes a bottom plate portion 11 , an axle core portion 12 and a connecting portion 13 , the bottom plate portion 11 is formed into an annular structure, and the bottom plate portion 11 is sleeved on the radial direction of the axle core portion 12 .
  • the connecting portion 13 is connected between the bottom plate portion 11 and the shaft core portion 12 , and the radial outer edge of the connecting portion 13 is connected with the bottom plate portion 11 , the radial inner edge of the connecting portion 13 is connected with the shaft core portion 12 .
  • the shaft core portion 2 is adapted to be connected with a motor, so as to be driven by the motor to realize the rotation of the centrifugal wind wheel 100 , a plurality of blades 2 are arranged on the bottom plate portion 11 , and a plurality of air inlet holes 10 are formed on the connecting portion 13 , In the radial direction of the hub 1 , the plurality of air inlet holes 10 are located between the shaft core portion 12 and the plurality of blades 2 .
  • the air inlet hole 10 extends in the radial direction of the hub 1 , the air inlet hole 10 has a profile line ⁇ 1 extending in the radial direction of the hub 1 , and the blade 2 has The bone line ⁇ 2 extending in the radial direction of the hub 1, on the cross section of the hub 1, the orthographic projection of the central axis 1a of the hub 1, the radially outer end point of the orthographic projection of the profile line ⁇ 1, and the diameter corresponding to the orthographic projection of the bone line ⁇ 2
  • the inner end points are located on the same straight line, then on the cross section of the hub 1, the orthographic projection of the central axis 1a of the hub 1, the radial outer end point of the orthographic projection of each profile line ⁇ 1 and the radial outer end of the orthographic projection of the corresponding bone line ⁇ 2
  • the inner end points are located on the same straight line, for example, in the example of FIG.
  • the position of the air inlet hole 10 is set reasonably, which is beneficial to further ensure the structural strength and the stability of the flow field of the centrifugal wind wheel 100, avoid abnormal noise and potential safety hazards during the rotation of the centrifugal wind wheel 100, and thus ensure the centrifugal wind wheel 100. sound quality and safety of use.
  • the profile line ⁇ 1 of the air inlet hole 10 can be understood as the center line of the outer contour shape of the orthographic projection of the air inlet hole 10 on the cross section of the hub 1, and the bone line ⁇ 2 of the blade 2 can be understood as the flow line along the blade 2
  • the cross-section of the wheel hub 1 is perpendicular to the center axis 1a of the wheel hub 1 .
  • the profile line ⁇ 1 is formed as a straight line, and the outer contour of the orthographic projection of the air inlet hole 10 on the cross section of the wheel hub 1 can be symmetrical about the profile line ⁇ 1 ;
  • the orthographic projection of the central axis 1a of the hub 1 On the cross section of 1, the orthographic projection of the central axis 1a of the hub 1, the radially outer end point of the orthographic projection of the profile line ⁇ 1, the radial inner end point of the orthographic projection of the profile line ⁇ 1, and the radial inner end point of the orthographic projection of the corresponding bone line ⁇ 2
  • the same straight line for example, in the example of FIG.
  • the orthographic projection O 1 of the central axis 1a of the hub 1, the radial outer end point O 3 of the orthographic projection of the profile line ⁇ 1, the profile line ⁇ 1 is positive
  • the radial inner end point O 4 of the projection and the radial inner end point O 2 of the orthographic projection of the corresponding bone line ⁇ 2 are located on the same straight line, then on the cross section of the hub 1, the orthographic projection of the central axis 1a of the hub 1 is the same as that of the bone line ⁇ 2.
  • the straight line formed by connecting the radially inner end points of the orthographic projection is collinear with the orthographic projection of the profile line ⁇ 1, thereby simplifying the structure of the air inlet hole 10, facilitating processing, and at the same time, it can further effectively weaken the structural strength of the air inlet hole 10 to the centrifugal wind wheel 100 influence, to ensure the reliable use of the centrifugal wind wheel 100.
  • the inventors of the present application have found through research and experimental verification that the width of the outer end of the air inlet hole 10 in the circumferential direction of the hub 1 will affect the air volume of the centrifugal wind wheel 100, so that the air inlet hole 10 is further reasonably arranged.
  • the radial inner end point of the orthographic projection of the bone line ⁇ 2 and the orthographic projection of the outer contour of the corresponding air inlet hole 10 on the circumference of the hub 1 are two points.
  • the side end points are respectively connected into a first straight line ⁇ 3 and a second straight line ⁇ 4, for example, the radial inner end point O 2 of the orthographic projection of the bone line ⁇ 2 and the orthographic projection of the outer contour of the corresponding air inlet hole 10 are on the circumferential side end point A of the hub 1.
  • first straight line ⁇ 3 is connected to form a first straight line ⁇ 3, and the radial inner end point O2 of the orthographic projection of the bone line ⁇ 2 and the orthographic projection of the outer contour of the corresponding air inlet hole 10 are connected to form a second
  • the angle formed between the straight line ⁇ 4, the first straight line ⁇ 3 and the second straight line ⁇ 4 towards the corresponding air inlet hole 10 is ⁇ , and ⁇ satisfies 120° ⁇ 135°, then the first straight line ⁇ 3 and the second straight line
  • the included angle formed between ⁇ 4 and facing away from the corresponding air inlet hole 10 is also ⁇ .
  • the inventor of the present application has verified through experiments that the included angle ⁇ is too large or too small for the centrifugal wind wheel 100.
  • the increase in air volume was not obvious.
  • the included angle ⁇ formed between the first straight line ⁇ 3 and the second straight line ⁇ 4 toward the corresponding air inlet hole 10 satisfies 120° ⁇ 135°, for example, ⁇ may be 125°, 129°, 130°, or 133° etc.
  • the distance between the radially inner end point of the profile ⁇ 1 and the central axis 1a of the hub 1 is L 0 , such as in the example of FIG. 5 .
  • the distance between the radial inner end O 4 of the profile ⁇ 1 and the central axis 1a of the hub 1 is L 0
  • L 0 satisfies L 0 ⁇ 0.3R, where R is the centrifugal fan 100
  • the radius of 100, that is, L 0 is greater than or equal to 30% of the radius of the centrifugal wind wheel 100, so as to avoid excessively setting the air inlet holes 10 to weaken the structural strength of the centrifugal wind wheel 100, and effectively ensure the structural strength of the centrifugal wind wheel 100 when it rotates.
  • the distance L 0 between the radial inner end point of the profile line ⁇ 1 and the central axis 1a of the hub 1 is greater than 30% of the radius of the centrifugal wind wheel 100, for example, the distance L 0 can be 0.33R, or 0.35R etc.
  • the radius of the centrifugal wind wheel 100 can be the outer edge radius of the reinforcement ring 3; when the centrifugal wind wheel 100 does not include the reinforcement ring 3, The radius of the centrifugal wind wheel 100 may be the radius of the hub 1; but it is not limited thereto.
  • the length of the profile ⁇ 1 is L 1
  • the length of the profile ⁇ 1 may be the radial inner end point O 4 of the profile ⁇ 1 and the diameter of ⁇ 1
  • the radial distance between the inward end points O 3 that is, the length of the air inlet hole 10 in the radial direction of the hub 1, L 1 satisfies 0.3L ⁇ L 1 ⁇ 0.2R, where L is the length of the blade 2 in the radial direction of the hub 1 , R is the radius of the centrifugal wind wheel 100, that is, L 1 is greater than or equal to 30% of the radial length of the blade 2 to effectively increase the air volume of the centrifugal wind wheel 100, and L 1 is less than or equal to 20% of the radius of the centrifugal wind wheel 100 to ensure centrifugal Structural strength of the wind turbine 100 .
  • the length L 1 of the profile ⁇ 1 satisfies 0.3L ⁇ L 1 ⁇ 0.2R, so as to effectively improve the air volume of the centrifugal rotor 100 on the premise of ensuring the structure of the centrifugal rotor 100 .
  • the distance between the radially outer end point of the profile line ⁇ 1 and the radially inner end point of the corresponding bone line ⁇ 2 is L 2 , for example at In the example of Fig.
  • the distance between the radially outer end point O3 of the profile line ⁇ 1 and the radially inner end point O2 of the corresponding bone line ⁇ 2 is L2
  • the distance L2 is the distance The shortest radial distance between the air hole 10 and the corresponding blade 2, where L 2 satisfies 1mm ⁇ L 2 ⁇ 0.3L, L is the length of the blade 2 in the radial direction of the hub 1, that is, L 2 is greater than or equal to 1mm and L 2 is less than or equal to 30% of the radial length of the blade 2, so as to ensure the power of the centrifugal wind wheel 100, so that the centrifugal wind wheel 100 has a good effect of rotating work.
  • the distance L 2 between the radially outer end point of the profile line ⁇ 1 and the radially inner end point of the corresponding bone line ⁇ 2 satisfies 1 mm ⁇ L 2 ⁇ 0.3L.
  • the centrifugal rotor 100 further includes a reinforcing ring 3 , the reinforcing ring 3 and the hub 1 are arranged at intervals along the axial direction of the hub 1 , and the reinforcing ring 3 and the hub 1 are respectively located on the blades 2 at both ends of the length, each blade 2 is connected between the hub 1 and the reinforcing ring 3, that is, one end of the length of the blade 2 is connected to the hub 1, and the other end of the length of the blade 2 is connected to the reinforcing ring 3, thereby improving the centrifugal wind. Structural strength of wheel 100.
  • the air treatment equipment according to the embodiment of the second aspect of the present application includes the centrifugal wind wheel 100 according to the embodiment of the first aspect of the present application.
  • the air treatment equipment may be an air conditioner, a dehumidifier, a humidifier, or an air purifier, etc.
  • the air treatment equipment may also be a combination of the above at least two kinds of equipment.
  • the air treatment equipment of the embodiment of the present application by using the centrifugal fan 100 described above, the air volume of the air treatment equipment is effectively improved, and the sound quality of the air treatment equipment is ensured at the same time.
  • the air treatment equipment is an air conditioner
  • the air treatment equipment has a fresh air duct, which can introduce outdoor fresh air into the room to realize indoor and outdoor air circulation
  • the centrifugal fan 100 is arranged in the fresh air duct.
  • the air conditioner has a fresh air module. Under the limitation of the size of the fresh air module, the strength of the mechanism and other factors, the centrifugal wind wheel 100 can effectively improve the ventilation air volume and ventilation efficiency of the air conditioner. sound quality.
  • a heat exchange device may not be installed in the fresh air duct. At this time, the fresh air duct has no heat exchange function and does not participate in cooling and heating. Of course, a heat exchange device can also be installed in the fresh air duct. At this time, the fresh air duct not only It has fresh air function and heat exchange function.
  • the terms “installed”, “connected” and “connected” should be understood in a broad sense, for example, it may be a fixed connection or a detachable connection Connection, or integral connection; can be mechanical connection, can also be electrical connection; can be directly connected, can also be indirectly connected through an intermediate medium, can be internal communication between two elements.
  • installed should be understood in a broad sense, for example, it may be a fixed connection or a detachable connection Connection, or integral connection; can be mechanical connection, can also be electrical connection; can be directly connected, can also be indirectly connected through an intermediate medium, can be internal communication between two elements.

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

Abstract

一种离心风轮(100)和具有其的空气处理设备，离心风轮(100)包括轮毂(1)和叶片(2)，轮毂(1)上形成有多个进风孔(10)，多个进风孔(10)沿轮毂(1)的周向间隔设置，每个进风孔(10)贯穿轮毂(1)，叶片(2)为多个，多个叶片(2)均设在轮毂(1)上，多个叶片(2)沿轮毂(1)的周向间隔设置且间隔设在多个进风孔(10)的径向外侧，叶片(2)的数量与进风孔(10)的数量相等，且每个叶片(2)与对应进风孔(10)沿轮毂(1)的径向相对设置。

Description

离心风轮和具有其的空气处理设备
相关申请的交叉引用
本申请基于申请号为202011044953.X、申请日为2020年09月28日的中国专利以及申请号为202022179591.7、申请日为2020年09月28日的中国专利申请提出，并要求上述中国专利申请的优先权，上述中国专利申请的全部内容在此引入本申请作为参考。
技术领域
本申请涉及空气处理装置技术领域，尤其是涉及一种离心风轮和具有其的空气处理设备。
背景技术
离心风轮依靠输入的机械能实现转动，从而提高气体压力并实现气体的排送。相关技术中，离心风轮的风量较低，换气效率较低。
发明内容
本申请旨在至少解决相关技术中存在的技术问题之一。为此，本申请提出一种离心风轮，所述离心风轮具有较大的换气风量和换气效率，且具有良好的声品质。
本申请还提出一种具有上述离心风轮的空气处理设备。
根据本申请第一方面实施例的离心风轮，包括：轮毂，所述轮毂上形成有多个进风孔，多个所述进风孔沿所述轮毂的周向间隔设置，每个所述进风孔贯穿所述轮毂；叶片，所述叶片为多个，多个所述叶片均设在轮毂上，多个所述叶片沿所述轮毂的周向间隔设置且间隔设在多个所述进风孔的径向外侧，所述叶片的数量与所述进风孔的数量相等，且每个所述叶片与对应所述进风孔沿所述轮毂的径向相对设置。
根据本申请实施例的离心风轮，通过在轮毂上形成多个进风孔，并使得进风孔的数量与叶片数量相等，且每个进风孔与对应叶片沿轮毂的径向相对设置，在保证离心风轮结构强度的同时，有效提升了离心风轮的换气风量及换气效率，同时保证了离心风轮的流场稳定，使得离心风轮具有良好的声品质。
在一些实施例中，所述进风孔沿所述轮毂的径向延伸且具有沿所述轮毂的径向延伸的型线，所述叶片具有沿所述轮毂的径向延伸的骨线，在所述轮毂的横截面上，所述轮 毂中心轴线的正投影、所述型线的正投影的径向外侧端点和对应所述骨线的正投影的径向内侧端点位于同一直线上。
在一些实施例中，所述型线形成为直线，在所述轮毂的横截面上，所述轮毂中心轴线的正投影、所述型线的正投影的径向外侧端点、所述型线的正投影的径向内侧端点和对应所述骨线的正投影的径向内侧端点位于同一直线上。
在一些实施例中，在所述轮毂的横截面上，所述骨线的正投影的径向内侧端点与对应所述进风孔的外轮廓的正投影在所述轮毂周向上的两侧端点分别连接成第一直线和第二直线，所述第一直线和所述第二直线之间形成的朝向对应所述进风孔的夹角为α，所述α满足：120°≤α≤135°。
在一些实施例中，在所述轮毂的径向上，所述型线的径向内侧端点与所述轮毂中心轴线之间的距离为L 0，所述L 0满足：L 0≥0.3R，其中，R为所述离心风轮的半径。
在一些实施例中，在所述轮毂的径向上，所述型线的长度为L 1，所述L 1满足：0.3L≤L 1≤0.2R，其中，L为所述叶片在所述轮毂径向上的长度，R为所述离心风轮的半径。
在一些实施例中，在所述轮毂的径向上，所述型线的径向外侧端点和对应所述骨线的径向内侧端点之间的距离为L 2，所述L 2满足：1mm≤L 2≤0.3L，L为所述叶片在所述轮毂径向上的长度。
在一些实施例中，所述离心风轮还包括：加强圈，所述加强圈和所述轮毂沿所述轮毂的轴向间隔设置，且分别位于所述叶片的长度两端。
根据本申请第二方面实施例的空气处理设备，包括根据本申请上述第一方面实施例的离心风轮。
根据本申请实施例的空气处理设备，通过采用上述的离心风轮，有效提升了空气处理设备的风量，同时保证了空气处理设备的声品质。
在一些实施例中，所述空气处理设备为空调器，且具有新风风道，所述离心风轮设于所述新风风道内。
本申请的附加方面和优点将在下面的描述中部分给出，部分将从下面的描述中变得明显，或通过本申请的实践了解到。
附图说明
本申请的上述和/或附加的方面和优点从结合下面附图对实施例的描述中将变得明显和容易理解，其中：
图1是根据本申请一个实施例的离心风轮的示意图；
图2是图1中圈示的A部的放大图；
图3是图1中所示的离心风轮的另一个示意图；
图4是图3中所述的离心风轮的又一个示意图；
图5是图4中圈示的B部的放大图；
图6是相关技术中的离心风轮的气流流动示意图。
附图标记：
离心风轮100、第一直线Ω3、第二直线Ω4、
轮毂1、中心轴线1a、
进风孔10、型线Ω1、
底板部11、轴芯部12、连接部13、
叶片2、离心风道20、骨线Ω2、
加强圈3。
具体实施方式
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。下面通过参考附图描述的实施例是示例性的，仅用于解释本申请，而不能理解为对本申请的限制。
下文的公开提供了许多不同的实施例或例子用来实现本申请的不同结构。为了简化本申请的公开，下文中对特定例子的部件和设置进行描述。当然，它们仅仅为示例，并且目的不在于限制本申请。此外，本申请可以在不同例子中重复参考数字和/或字母。这种重复是为了简化和清楚的目的，其本身不指示所讨论各种实施例和/或设置之间的关系。此外，本申请提供了的各种特定的工艺和材料的例子，但是本领域普通技术人员可以意识到其他工艺的可应用于性和/或其他材料的使用。
下面，参考附图描述根据本申请第一方面实施例的离心风轮100。
如图1所示，离心风轮100包括轮毂1和叶片2，轮毂1上形成有多个进风孔10，多个进风孔10沿轮毂1的周向间隔设置，每个进风孔10贯穿轮毂1，叶片2为多个，多个叶片2均设在轮毂1上，多个叶片2沿轮毂1的周向间隔设置，相邻两个叶片2之间限定出离心风道20，离心风道20与进风孔10连通，且多个叶片2间隔设在多个进风孔10的径向外侧，则在轮毂1的径向上，多个进风孔10位于多个叶片2的内侧。
由此，离心风轮100转动，一部分气流通过进风孔10流至多个叶片2内侧，还有一部分气流通过叶片2的远离轮毂1的一端流至多个叶片2内侧，这两部分气流均通过 离心风道20流出，从而增加了离心风轮100的进气面积，有效提升了离心风轮100的换气风量，从而提升了离心风轮100的换气效率，而且轮毂1适于与电机相连，通过进风孔10流至叶片2内侧的气流还可以对电机进行有效散热，以给电机降温。在本申请的描述中，“多个”的含义是两个或两个以上。
其中，如图3和图4所示，叶片2的数量与进风孔10的数量相等，则每个叶片2分别对应一个进风孔10，每个进风孔10分别对应一个叶片2，使得多个进风孔10和多个叶片2分别一一对应设置；每个叶片2与对应进风孔10沿轮毂1的径向相对设置，则在轮毂1的径向上，每个叶片2分别设在对应进风孔10的外侧，而由于离心风轮100为旋转部件，则通过进风孔10流出的气流可以更加平和地流入离心风道20内进行加速，避免离心风轮100的流场因设置进风孔10而不稳定、导致产生异音，从而保证了离心风轮100的流场稳定性，进而保证离心风轮100转动过程中不产生其他异音，使得离心风轮100具有良好的声品质，保证用户体验。
需要说明的是，方向“外”是指沿轮毂1的径向远离轮毂1中心轴线1a的方向，其相反方向被定义为“内”。
根据本申请实施例的离心风轮100，通过在轮毂1上形成多个进风孔10，并使得进风孔10的数量与叶片2数量相等，且每个进风孔10与对应叶片2沿轮毂1的径向相对设置，在保证离心风轮100结构强度的同时，有效提升了离心风轮100的换气风量及换气效率，同时保证了离心风轮100的流场稳定，使得离心风轮100具有良好的声品质。由此，本申请可以在不改变离心风轮100整体结构尺寸的前提下，提升离心风轮100的换气效率和稳定性，便于使得离心风轮100具有良好的适用性和实用性。
本申请发明人通过将本申请实施例的离心风轮100与相关技术中未设置进风孔的离心风轮进行实验对比，结果得到，在相同转速下，本申请中的离心风轮100相比于相关技术中的离心风轮的风量有显著提升，且风量提升可以达到10％，而且经验证，本申请的离心风轮100在运转过程中没有产生异音，频谱及听感均无异常，且满足跌落要求，没有安全隐患，具有良好的使用可靠性。
此外，一些技术中，出于电机散热或减重的考虑，在离心风轮的轮廓上设置开孔，开孔的设置方式没有依据且比较随意，例如无论什么结构的离心风轮，通常轮毂上的开孔为6个，使得离心风轮的风量提升受限。本申请中将进风孔10的数量设置与叶片2数量相等，且使得每个进风孔10与对应叶片2沿轮毂1径向相对设置，以在保证离心风轮100结构强度的同时，进一步提升了风量，且使得离心风轮100流场稳定，避免离心风轮100产生其他异音。
例如，图6中展示了一些技术中轮毂开口6个开孔的离心风轮的流动状态差异。在具有6个开孔的离心风轮中，由于开孔过大，如果将相邻叶片之间构成的区域看成一个风道的话，会导致单个风道内流入的气体流向差异过大，而在整个风道内气流偏转角度β2-β1(其中β2为气流出气角，β1为气流进气角)往往在75°左右，如此大的气流流向变动会导致流向差异较大的气流的流动损失更加明显，这样便会抵消大开孔引入气流的能量，从而无法有效地提升风量；而本申请中进风孔10流入的气流可以顺着叶片2的型线Ω1方向逐渐流动，由于流体的附壁效应，其流动状态更加稳定，流动损失更小，单个叶片2的做功效率更高，从而带来更大的风量。
此外，对于高速运转的离心风轮，例如直径为0.1m、转速为2400rpm时，离心风轮会受到大约自身质量3000倍的拉力。在这种前提下，上述技术中开孔为6个的方案就更不成立了，因为叶片强度远不能满足高速运转要求。而本申请中与叶片2数量呈1:1的进风孔10，离心风轮100结构强度经实验验证完全满足要求。
其中，本申请发明人进行了如下实验验证：选取直径为0.13m的离心风轮，实验项目如下表1所示，表格中“相关技术一”是指未设置进风孔的离心风轮，“相关技术二”是指设置6个开孔的离心风轮。从表中可以明显看出，在相同转速下，本申请离心风轮100风量有显著提升，而且没有异音和安全隐患，与未设置进风孔的离心风轮和设置6个开孔的离心风轮相比，本申请离心风轮100具有明显技术优势。
表1 本申请与相关技术的实验验证结果对比
测试项目 相关技术一 相关技术二 本申请
风量 53m 3/h 55m 3/h 60m 3/h
噪音 49dB 49.2dB 49.2dB
强度 2400rpm时，无断裂 2400rpm时，断裂 2400rpm时，无断裂
例如，在图1和图3的示例中，轮毂1包括底板部11、轴芯部12和连接部13，底板部11形成为环状结构，底板部11套设在轴芯部12的径向外侧，且底板部11与轴芯部12沿轮毂1的径向间隔设置，连接部13连接在底板部11和轴芯部12之间，则连接部13的径向外边沿与底板部11相连，连接部13的径向内边沿与轴芯部12相连。其中，轴芯部2适于与电机相连，以由电机驱动实现离心风轮100的转动，多个叶片2均设在底板部11上，多个进风孔10均形成在连接部13上，则在轮毂1的径向上，多个进风孔10位于轴芯部12和多个叶片2之间。
在一些实施例中，如图2、图4和图5所示，进风孔10沿轮毂1的径向延伸，进风孔10具有沿轮毂1的径向延伸的型线Ω1，叶片2具有沿轮毂1的径向延伸的骨线Ω2， 在轮毂1的横截面上，轮毂1中心轴线1a的正投影、型线Ω1的正投影的径向外侧端点和对应骨线Ω2的正投影的径向内侧端点位于同一直线上，则在轮毂1的横截面上，轮毂1中心轴线1a的正投影、每个型线Ω1的正投影的径向外侧端点和对应骨线Ω2的正投影的径向内侧端点位于同一直线上，例如在图5的示例中，在轮毂1的横截面上，轮毂1中心轴线1a的正投影O 1、型线Ω1的正投影的径向外侧端点O 3和对应骨线Ω2的正投影的径向内侧端点O 2位于同一直线上；换言之，在轮毂1的横截面上，多个叶片2所在柱面的轴线的正投影、型线Ω1的正投影的径向外侧端点和对应骨线Ω2的正投影的径向内侧端点位于同一直线上。由此，进风孔10的位置设置合理，有利于进一步保证离心风轮100的结构强度和流场稳定，避免离心风轮100转动过程中产生异音和安全隐患，从而保证了离心风轮100的声品质和使用安全性。
需要说明的是，进风孔10的型线Ω1可以理解为进风孔10在轮毂1横截面上的正投影的外轮廓形状的中线，叶片2的骨线Ω2可以理解为叶片2沿流线方向截面形状的中线，轮毂1的横截面与轮毂1的中心轴线1a垂直。
在一些实施例中，如图2、图4和图5所示，型线Ω1形成为直线，进风孔10在轮毂1横截面上的正投影的外轮廓可以关于型线Ω1对称；在轮毂1的横截面上，轮毂1中心轴线1a的正投影、型线Ω1的正投影的径向外侧端点、型线Ω1正投影的径向内侧端点和对应骨线Ω2的正投影的径向内侧端点位于同一直线上，例如在图5的示例中，在轮毂1的横截面上，轮毂1中心轴线1a的正投影O 1、型线Ω1的正投影的径向外侧端点O 3、型线Ω1正投影的径向内侧端点O 4和对应骨线Ω2的正投影的径向内侧端点O 2位于同一直线上，则在轮毂1的横截面上，轮毂1中心轴线1a的正投影和骨线Ω2的正投影的径向内侧端点连接形成的直线与型线Ω1的正投影共线，从而简化了进风孔10的结构，便于加工，同时可以进一步有效削弱进风孔10对离心风轮100结构强度的影响，保证离心风轮100使用可靠。
此外，本申请发明人经过研究发现，经过实验验证发现，进风孔10外端在轮毂1周向上的宽度大小会影响离心风轮100的风量，从而进一步合理设置进风孔10。在一些实施例中，如图5所示，在轮毂1的横截面上，骨线Ω2的正投影的径向内侧端点与对应进风孔10的外轮廓的正投影在轮毂1周向上的两侧端点分别连接成第一直线Ω3和第二直线Ω4，例如骨线Ω2的正投影的径向内侧端点O 2与对应进风孔10外轮廓的正投影在轮毂1周向一侧端点A 1连线形成第一直线Ω3，骨线Ω2的正投影的径向内侧端点O 2与对应进风孔10外轮廓的正投影在轮毂1周向另一侧端点A 2连线形成第二直线Ω4，第一直线Ω3和第二直线Ω4之间形成的朝向上述对应进风孔10的夹角为α，α满 足120°≤α≤135°，则第一直线Ω3和第二直线Ω4之间形成的背向对应进风孔10的夹角也为α。由此，通过设置夹角α，使得进风孔10设置更加合理，从而有效提升离心风轮100的风量，而且本申请发明人经实验验证，夹角α过大或过小对于离心风轮100风量的提升均不明显。
可选地，第一直线Ω3和第二直线Ω4之间形成的朝向对应进风孔10的夹角α满足120°＜α＜135°，例如α可以为125°、129°、130°、或133°等。
在一些实施例中，如图4和图5所示，在轮毂1的径向上，型线Ω1的径向内侧端点与轮毂1中心轴线1a之间的距离为L 0，例如在图5的示例中，在轮毂1的径向上，型线Ω1的径向内侧端点O 4与轮毂1中心轴线1a之间的距离为L 0，L 0满足L 0≥0.3R，其中，R为离心风轮100的半径，即L 0大于等于离心风轮100半径的30％，以避免进风孔10的设置过多削弱离心风轮100的结构强度，有效保证了离心风轮100旋转时的结构强度。
可选地，在轮毂1的径向上，型线Ω1的径向内侧端点与轮毂1中心轴线1a之间的距离L 0大于离心风轮100半径的30％，例如距离L 0可以为0.33R、或0.35R等。
可以理解的是，当离心风轮100包括加强圈3时，如图4所示，离心风轮100的半径可以为加强圈3的外边沿半径；当离心风轮100不包括加强圈3时，离心风轮100的半径可以为轮毂1的半径；但不限于此。
在一些实施例中，如图4和图5所示，在轮毂1的径向上，型线Ω1的长度为L 1，型线Ω1的长度可以为型线Ω1径向内侧端点O 4和Ω1径向内侧端点O 3之间的径向距离，即进风孔10在轮毂1径向上的长度，L 1满足0.3L≤L 1≤0.2R，其中，L为叶片2在轮毂1径向上的长度，R为离心风轮100的半径，即L 1大于等于叶片2径向长度的30％，以有效提升离心风轮100的风量，且L 1小于等于离心风轮100半径的20％，保证离心风轮100的结构强度。
可选地，在轮毂1的径向上，型线Ω1的长度L 1满足0.3L＜L 1＜0.2R，以在保证离心风轮100结构的前提下，有效提升了离心风轮100的风量。
在一些实施例中，如图4和图5所示，在轮毂1的径向上，型线Ω1的径向外侧端点和对应骨线Ω2的径向内侧端点之间的距离为L 2，例如在图5的示例中，在轮毂1的径向上，型线Ω1的径向外侧端点O 3和对应骨线Ω2的径向内侧端点O 2之间的距离为L 2，则距离为L 2为进风孔10与对应叶片2之间的最短径向距离，其中L 2满足1mm≤L 2≤0.3L，L为叶片2在轮毂1径向上的长度，即L 2大于等于1mm且L 2小于等于叶片2径向长度的30％，从而保证离心风轮100的功率，使得离心风轮100具有良好的旋转做功效果。
可选地，在轮毂1的径向上，型线Ω1的径向外侧端点和对应骨线Ω2的径向内侧端点之间的距离L 2满足1mm＜L 2＜0.3L。
在一些实施例中，如图1和图3所示，离心风轮100还包括加强圈3，加强圈3和轮毂1沿轮毂1的轴向间隔设置，且加强圈3和轮毂1分别位于叶片2的长度两端，则每个叶片2连接在轮毂1和加强圈3之间，即叶片2的长度一端与轮毂1相连，叶片2的长度另一端与加强圈3相连，从而提升了离心风轮100的结构强度。
根据本申请第二方面实施例的空气处理设备，包括根据本申请上述第一方面实施例的离心风轮100。其中，空气处理设备可以为空调器、除湿机、加湿器、或空气净化器等，当然空气处理设备还可以为上述至少两种设备的组合。
根据本申请实施例的空气处理设备，通过采用上述的离心风轮100，有效提升了空气处理设备的风量，同时保证了空气处理设备的声品质。
在一些实施例中，空气处理设备为空调器，且空气处理设备具有新风风道，新风风道可以将室外新风引入室内，实现室内室外空气流通，离心风轮100设于新风风道内。例如，空调器具有新风模块，在新风模块尺寸、机构强度等因素的限制下，离心风轮100可以有效提升空调器的换气风量和换气效率，使用可靠、且保证了空调器具有良好的声品质。
可以理解的是，新风风道内可以不设置换热装置，此时新风风道不具有换热功能，不参与制冷制热；当然，新风风道内也可以设置换热装置，此时新风风道不仅具有新风功能，还具有换热功能。
根据本申请实施例的空气处理设备的其他构成以及操作对于本领域普通技术人员而言都是已知的，这里不再详细描述。
在本申请的描述中，需要理解的是，术语“中心”、“横向”、“长度”、“宽度”、“厚度”、“内”、“外”、“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。
在本申请的描述中，需要说明的是，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或一体地连接；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。对于本领域的普通技术人员而言，可以具体情况理解上述术语在本申请中的具体含义。
在本说明书的描述中，参考术语“一个实施例”、“一些实施例”、“示意性实施例”、“示例”、“具体示例”、或“一些示例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或者特点包含于本申请的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不一定指的是相同的实施例或示例。而且，描述的具体特征、结构、材料或者特点可以在任何的一个或多个实施例或示例中以合适的方式结合。
尽管已经示出和描述了本申请的实施例，本领域的普通技术人员可以理解：在不脱离本申请的原理和宗旨的情况下可以对这些实施例进行多种变化、修改、替换和变型，本申请的范围由权利要求及其等同物限定。

Claims (10)

  1. 一种离心风轮，其中，包括：
    轮毂，所述轮毂上形成有多个进风孔，多个所述进风孔沿所述轮毂的周向间隔设置，每个所述进风孔贯穿所述轮毂；
    叶片，所述叶片为多个，多个所述叶片均设在轮毂上，多个所述叶片沿所述轮毂的周向间隔设置且间隔设在多个所述进风孔的径向外侧，所述叶片的数量与所述进风孔的数量相等，且每个所述叶片与对应所述进风孔沿所述轮毂的径向相对设置。
  2. 根据权利要求1所述的离心风轮，其中，所述进风孔沿所述轮毂的径向延伸且具有沿所述轮毂的径向延伸的型线，所述叶片具有沿所述轮毂的径向延伸的骨线，在所述轮毂的横截面上，所述轮毂中心轴线的正投影、所述型线的正投影的径向外侧端点和对应所述骨线的正投影的径向内侧端点位于同一直线上。
  3. 根据权利要求2所述的离心风轮，其中，所述型线形成为直线，在所述轮毂的横截面上，所述轮毂中心轴线的正投影、所述型线的正投影的径向外侧端点、所述型线的正投影的径向内侧端点和对应所述骨线的正投影的径向内侧端点位于同一直线上。
  4. 根据权利要求1-3中任一项所述的离心风轮，其中，在所述轮毂的横截面上，所述骨线的正投影的径向内侧端点与对应所述进风孔的外轮廓的正投影在所述轮毂周向上的两侧端点分别连接成第一直线和第二直线，所述第一直线和所述第二直线之间形成的朝向对应所述进风孔的夹角为α，所述α满足：120°≤α≤135°。
  5. 根据权利要求1-4中任一项所述的离心风轮，其中，在所述轮毂的径向上，所述型线的径向内侧端点与所述轮毂中心轴线之间的距离为L 0，所述L 0满足：L 0≥0.3R，其中，R为所述离心风轮的半径。
  6. 根据权利要求1-5中任一项所述的离心风轮，其中，在所述轮毂的径向上，所述型线的长度为L 1，所述L 1满足：0.3L≤L 1≤0.2R，其中，L为所述叶片在所述轮毂径向上的长度，R为所述离心风轮的半径。
  7. 根据权利要求1-6中任一项所述的离心风轮，其中，在所述轮毂的径向上，所述型线的径向外侧端点和对应所述骨线的径向内侧端点之间的距离为L 2，所述L 2满足：1mm≤L 2≤0.3L，L为所述叶片在所述轮毂径向上的长度。
  8. 根据权利要求1-7中任一项所述的离心风轮，其中，还包括：
    加强圈，所述加强圈和所述轮毂沿所述轮毂的轴向间隔设置，且分别位于所述叶片的长度两端。
  9. 一种空气处理设备，其中，包括根据权利要求1-8中任一项所述的离心风轮。
  10. 根据权利要求9中的空气处理设备，其中，所述空气处理设备为空调器，且具有新风风道，所述离心风轮设于所述新风风道内。
PCT/CN2020/128977 2020-09-28 2020-11-16 离心风轮和具有其的空气处理设备 WO2022062130A1 (zh)

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