Centrifugal fans and range hoods including them

Abstract

This invention discloses a centrifugal fan and a range hood including the same. The centrifugal fan includes a volute, an air inlet disposed on the volute, an impeller disposed within the volute, and an air inlet ring connected to the volute. The centrifugal fan also includes a first sealing member and a second sealing member, wherein the first sealing member is connected or indirectly connected to the front end of the impeller; the second sealing member is directly or indirectly fixed to the inner side of the air inlet ring; the first sealing member and the second sealing member extend circumferentially around the axis of the impeller, and the first sealing member and the second sealing member are sealed together to block the gap between the air inlet ring and the front end of the impeller. This invention eliminates aerodynamic performance loss caused by airflow leakage and improves fan efficiency when various conventional optimization conditions cannot be further optimized.

Description

Technical Field

[0001] This invention relates to centrifugal fans and range hoods including the same. Background Technology

[0002] Centrifugal fans are widely used in various fields, such as range hoods, where they are commonly used to extract cooking fumes. For example, the centrifugal fan disclosed in Chinese patent application CN219691821U includes a volute and an impeller disposed within the volute. The rotation of the impeller causes gas to flow from outside the volute into the air inlet and then into the volute. The air inlet ring at the air inlet guides the airflow.

[0003] The advantages of current centrifugal fans are high static pressure and low noise. However, their aerodynamic efficiency is relatively low compared to other turbomachinery. For example, the aerodynamic efficiency of forward-curved multi-blade fans is generally 55% to 58%, which is quite low. Conventional optimization methods, such as optimizing blade parameters, matching volute profile design, or optimizing inlet and outlet resistance, have limitations, leaving little room for further improvement and preventing further enhancement of aerodynamic efficiency. Summary of the Invention

[0004] The technical problem to be solved by the present invention is to overcome the shortcomings of low aerodynamic efficiency and limited optimization space of centrifugal fans in the prior art.

[0005] The present invention solves the above-mentioned technical problems through the following technical solution:

[0006] A centrifugal fan includes a volute, an air inlet disposed on the volute, an impeller disposed inside the volute, and an air inlet ring connected to the volute. The centrifugal fan further includes a first sealing member and a second sealing member, wherein the first sealing member is connected or indirectly connected to the front end of the impeller; the second sealing member is directly or indirectly fixed to the inner side of the air inlet ring; the first sealing member and the second sealing member extend circumferentially around the axis of the impeller, and the first sealing member and the second sealing member are sealed together and block the gap between the air inlet ring and the front end of the impeller.

[0007] In this solution, by sealing the space between the inlet ring and the front end of the impeller, the airflow coming out from the circumference of the impeller can no longer leak through the gap between the inlet ring and the front end of the impeller. This avoids secondary flow between the front disc and the inlet ring of the centrifugal fan, eliminates the aerodynamic performance loss caused by airflow leakage, and improves the efficiency of the fan when various conventional optimization conditions cannot be further optimized.

[0008] Preferably, the first and second sealing members do not contact each other, wherein the first and second sealing members are spaced apart along the axial direction and their projections along the axial direction at least partially overlap. This axial overlap increases the difficulty of airflow outflow. Most of the airflow exiting from the second sealing member is directly blocked by the protruding second sealing member due to the overlap, preventing it from flowing out. The remaining small portion of airflow is slowed and has a small outflow volume due to the meandering interval between the first and second sealing members. Therefore, overall, considerable airflow leakage is still significantly prevented, ensuring improved fan efficiency. Furthermore, the non-contacting first and second sealing members do not interfere with each other's movement, avoiding wear.

[0009] Preferably, the first sealing member and the second sealing member are in contact with and sealed to each other, and / or the second sealing member and the air inlet ring are in contact with and sealed to each other. By sealing with both the first sealing member and the air inlet ring, the second sealing member can completely prevent any airflow from passing through the gap between the second sealing member and the first sealing member, and the gap between the second sealing member and the air inlet ring, thereby maximizing fan efficiency.

[0010] Preferably, the second or first sealing member is provided with a sealing groove, and at least a portion of the first or second sealing member mates with the sealing groove. The sealing groove provides a more complete seal for the first or second sealing member, and the sealing effect can be achieved without additional auxiliary sealing media.

[0011] Preferably, the second or first sealing member includes an axial end edge extending along the axial direction, the sealing groove being axially recessed and annular in shape, and the sidewalls of the sealing groove fitting against both sides of the axial end edge. The axial end edge can thus rotate within the annular sealing groove, thereby ensuring relative movement between the first and second sealing members while sealing. The sidewalls of the sealing groove also provide support for the axial end edge, ensuring that the axial end edge of the cantilever structure in the axial direction is supported and restricted even at its extended point, thus guaranteeing a certain level of seismic resistance and strength for the first sealing member under high-speed impeller operation.

[0012] Preferably, the first sealing member is connected to the front end of the impeller via a vibration damping mechanism, and / or the second sealing member is connected to the air inlet ring via a vibration damping mechanism, wherein the vibration damping mechanism is configured to absorb vibrations in the radial and / or axial directions. The vibration damping mechanism can reduce axial vibrations and radial runouts generated during impeller operation.

[0013] Preferably, the damping mechanism includes a body component and an elastic component. The two ends of the body component are respectively connected to the first sealing component and the front end of the impeller, or the two ends of the body component are respectively connected to the sealing component and the air inlet ring. This avoids the first sealing component or the second sealing component from fatigue failure due to vibration, and also avoids interference and jamming between the first sealing component and the second sealing component, which could cause greater damage.

[0014] Preferably, the elastic component includes a linear spring and a disc spring. The linear spring is a positive stiffness element with a stiffness coefficient k > 0; the disc spring is a negative stiffness element with a stiffness coefficient k < 0. After the linear spring and the disc spring are vector-combined, within a certain speed range, the stiffness coefficient k of the load and displacement can be made close to 0, thereby minimizing the displacement change of the first sealing component and the second sealing component within the corresponding dynamic stiffness range, isolating the vibration transmitted from the moving impeller to the air inlet ring, and ensuring that airflow leakage is reduced during impeller rotation while minimizing the vibration of the centrifugal fan.

[0015] Preferably, a damping washer and / or a flat washer are sequentially disposed between the linear spring and the disc spring. The flat washer provides a smooth contact surface, resulting in more stable contact between the linear spring and the disc spring, and also stabilizes the coefficient of friction of the supporting surface. This helps reduce seizing caused by localized contact and improves the reliability of the connection. The damping washer has excellent shock absorption properties, effectively absorbing vibrations and reducing noise generation.

[0016] Preferably, the main body component has a columnar body and a surrounding wall encircling the outside of the columnar body, forming a surrounding space between the surrounding wall and the columnar body. The linear spring, the disc spring, the damping washer, and / or the flat washer are all sleeved on the columnar body, and the disc spring, the damping washer, and / or the flat washer are accommodated within the surrounding space. Thus, the disc spring, the damping washer, and / or the flat washer can be limited and protected.

[0017] Preferably, the connection at at least one end of the main body component is restricted to axial and / or radial mobility. This allows the main body component to move in the axial and / or radial directions, thereby enabling the connected first and / or second sealing components to move to accommodate the fit, thus preventing structural compression and damage caused by misfitting the first and second sealing components in the radial and / or axial directions. Simultaneously, when the fit stiffness coefficient k is close to 0, the entire damping mechanism can still be displaced relative to the first and / or second sealing components in the radial and / or axial directions to accommodate vibrations and larger-amplitude movements.

[0018] Preferably, the second sealing member has a movable groove formed on the side facing the air inlet ring. A connecting cover is placed over the movable groove. One end of the main body member is restricted by the connecting cover within the movable groove to move in the axial and radial directions. The other end of the main body member is fixedly connected to the air inlet ring. The movable groove provides space for the main body member to move, facilitating a reduction in the installation accuracy of the shock-absorbing component. If the movable groove is further configured as an annular shape, it can further provide movement around the axial direction, further reducing the accuracy requirements of the installation position.

[0019] Preferably, the second sealing member or the first sealing member is provided with a sealing groove, and at least a portion of the first sealing member or the second sealing member mates with the sealing groove. The connection position of the damping mechanism is aligned with the sealing groove. This allows the damping mechanism to directly bear the axial force acting on the sealing groove, thereby more directly absorbing axial vibrations and avoiding shear forces on the first sealing member or the second sealing member.

[0020] Preferably, the first sealing member includes a radial end edge extending along the radial direction, and the impeller includes a plurality of blades. The radial end edge extends radially and connects to the ends of each of the blades. Thus, the radial end edge not only serves as part of the first sealing member but also connects and fixes the blades at the front end of the impeller, and the radial end edge can also block part of the airflow.

[0021] Preferably, the second sealing member has a movable groove on the side facing the air inlet ring, the movable groove being used to connect with the shock absorption mechanism. The second sealing member also has a sealing groove on the side facing the front end of the impeller, the sealing groove being used to cooperate with the first sealing member. The air inlet ring has an inner extension section extending towards the impeller, and the second sealing member is in a sealing fit with the inner extension section. The extension lengths of the inner extension section and the sealing groove at least partially overlap in the axial direction. This allows the material between the movable groove and the sealing groove of the second sealing member to be supported by the inner extension section of the air inlet ring, and the movable groove and the sealing groove to be damaged at their weakest point when subjected to radial force.

[0022] A range hood includes the centrifugal fan.

[0023] The positive and progressive effects of this invention are: it eliminates the aerodynamic performance loss caused by airflow leakage, and improves the efficiency of the fan when various conventional optimization conditions cannot be further optimized. Attached Figure Description

[0024] Figure 1This is a three-dimensional structural diagram of a centrifugal fan according to a preferred embodiment of the present invention.

[0025] Figure 2 This is a cross-sectional structural diagram of a centrifugal fan according to a preferred embodiment of the present invention.

[0026] Figure 3 for Figure 2 Enlarged schematic diagram of part A in the diagram.

[0027] Figure 4 This is an exploded structural diagram of a centrifugal fan according to a preferred embodiment of the present invention.

[0028] Figure 5 This is a three-dimensional schematic diagram of the first sealing component according to a preferred embodiment of the present invention.

[0029] Figure 6 This is a three-dimensional structural schematic diagram of the second sealing component according to a preferred embodiment of the present invention.

[0030] Figure 7 This is another three-dimensional structural schematic diagram of the second sealing member according to a preferred embodiment of the present invention.

[0031] Figure 8 This is a three-dimensional structural diagram of the shock absorption mechanism according to a preferred embodiment of the present invention.

[0032] Figure 9 This is a cross-sectional structural diagram of the shock absorption mechanism according to a preferred embodiment of the present invention.

[0033] Figure 10 This is an exploded structural diagram of the shock absorption mechanism according to a preferred embodiment of the present invention.

[0034] Explanation of reference numerals in the attached figures

[0035] Impeller 100

[0036] Front-end 101

[0037] Leaf 110

[0038] 200mm air inlet ring

[0039] Inner extension 210

[0040] First sealing component 300

[0041] Axial end edge 310

[0042] Radial edge 320

[0043] Second sealing component 400

[0044] Sealing groove 410

[0045] Moving groove 420

[0046] Connecting cover 430

[0047] 500 shock absorption mechanism

[0048] Body component 510

[0049] Column body 511

[0050] Surrounding Wall 512

[0051] Surround Space 513

[0052] Protrusion 514

[0053] Threaded part 515

[0054] Linear Spring 520

[0055] Disc spring 530

[0056] Damping pad 540

[0057] Flat gasket 550

[0058] 600 volute

[0059] Air inlet 610

[0060] Gap 700

[0061] Axis X

[0062] Overlap distance B Detailed Implementation

[0063] The present invention will be further illustrated by way of embodiments below, but the present invention is not limited to the scope of the embodiments described herein.

[0064] like Figures 1-10 As shown, this embodiment discloses a centrifugal fan, including a volute 600, an air inlet 610 disposed on the volute 600, an impeller 100 disposed inside the volute 600, and an air inlet ring 200 connected to the volute 600. The centrifugal fan also includes a first sealing member 300 and a second sealing member 400, wherein the first sealing member 300 is connected or indirectly connected to the front end 101 of the impeller 100; the second sealing member 400 is directly or indirectly fixed to the inner side of the air inlet ring 200; the first sealing member 300 and the second sealing member 400 extend circumferentially around the axis X of the impeller 100, and the first sealing member 300 and the second sealing member 400 are sealed together and seal the gap 700 between the air inlet ring 200 and the front end 101 of the impeller 100.

[0065] like Figure 1As shown, in this embodiment, the air inlet 610 of the volute 600 is a circular opening. An air inlet ring 200 is connected to the volute 600. The air inlet ring 200 has a guiding surface shape, allowing air to enter the impeller 100 within the air inlet 610 through the surface of the air inlet ring 200, for example, an arc shape. The axis X is typically the rotation axis of the impeller 100. The relative connection and arrangement of the air inlet ring 200, the volute 600, and the impeller 100 can be adjusted according to known related designs.

[0066] like Figure 2 and Figure 3 As shown, in this embodiment, the air inlet ring 200 and the front end 101 of the impeller 100 are aligned in the X-axis direction ( Figure 2 and Figure 3 There is a distance between the air inlet ring 200 and the impeller 100 in the vertical direction to ensure that they do not interfere with each other. The distance between the front end 101 of the air inlet ring 200 and the impeller 100 in the X-axis direction forms a gap 700. When the gap 700 is not closed, specifically for example... Figure 3 The airflow in the left-right direction (radial direction of impeller 100) can flow freely. The notch 700 is essentially an annular space. After the airflow from the centrifugal fan enters the impeller 100, some of the airflow will flow along, for example... Figure 2 and Figure 3 The airflow follows the direction of the arrow drawn in the middle. This portion of the airflow flows out from the gaps in the blades 110 on the outer periphery of the impeller 100 and flows into the front end of the volute 600. Figure 2 The gap between the upper surface of the impeller 100 and the front end 101 of the impeller 100. If the first sealing member 300 and the second sealing member 400 are not provided to block the gap 700, the airflow passes through the gap between the front end 101 of the impeller 100 and the air inlet ring 200, and then flows out of the volute 600 from the gap 700.

[0067] In this embodiment, the sealing of the gap 700 by the first sealing member 300 and the second sealing member 400 can be a completely airtight seal, meaning that the first sealing member 300 and the second sealing member 400 are fitted together with an interference fit so that there is no gap between them. Alternatively, it can completely seal the gap 700, with only a small amount of gas escaping from the gap between the first sealing member 300 and the second sealing member 400. That is, the first sealing member 300 and the second sealing member 400 are fitted together with a transition fit, or they are tightly attached, or other methods are used to block the escape of airflow to achieve a general seal.

[0068] In this embodiment, by sealing the gap 700 between the air inlet ring 200 and the front end 101 of the impeller 100, the airflow coming out from the periphery of the impeller 100 can no longer leak through the gap 700 between the air inlet ring 200 and the front end 101 of the impeller 100. This avoids secondary flow between the front plate of the centrifugal fan and the air inlet ring 200, eliminates the aerodynamic performance loss caused by airflow leakage, and achieves improved fan efficiency when various conventional optimization conditions cannot be further optimized.

[0069] In some alternative embodiments, the first sealing member 300 and the second sealing member 400 do not contact each other, wherein the first sealing member 300 and the second sealing member 400 are spaced apart along the X-axis and their projections along the X-axis at least partially overlap. This overlap along the X-axis increases the difficulty of airflow outflow. Most of the airflow exiting from the second sealing member 400 is directly blocked by the protruding second sealing member 400 due to the overlap, thus preventing it from flowing out. The remaining small portion of airflow has a slow velocity and small outflow volume due to the meandering interval between the first sealing member 300 and the second sealing member 400. Therefore, overall, considerable airflow leakage is still significantly prevented, ensuring improved fan efficiency. Furthermore, the non-contact nature of the first sealing member 300 and the second sealing member 400 prevents motion interference and avoids wear.

[0070] like Figure 3 As shown, in a preferred embodiment, the first sealing member 300 and the second sealing member 400 are in contact with and sealed to each other, and / or the second sealing member 400 and the inlet ring 200 are in contact with and sealed to each other. By sealing with both the first sealing member 300 and the inlet ring 200, the second sealing member 400 can completely prevent any airflow from passing through the gap between the second sealing member 400 and the first sealing member 300, and the gap between the second sealing member 400 and the inlet ring 200, thereby maximizing fan efficiency.

[0071] like Figures 3-7 As shown, in a further preferred embodiment, the second sealing member 400 is provided with a sealing groove 410, and at least a portion of the corresponding first sealing member 300 mates with the sealing groove 410. The sealing groove 410 provides a more complete seal for the first sealing member 300 or the second sealing member 400, and the sealing effect can be achieved without additional auxiliary sealing media through the sealing groove 410.

[0072] like Figures 3-7As shown, in a further preferred embodiment, the first sealing member 300 includes an axial end edge 310 extending along the X-axis, and a sealing groove 410 that is axially recessed and annular in shape, with the sidewalls of the sealing groove 410 fitting against both sides of the axial end edge 310. The axial end edge 310 can thus rotate within the annular sealing groove 410, thereby ensuring relative movement between the first sealing member 300 and the second sealing member 400 while maintaining a seal. The sidewalls of the sealing groove 410 also provide support for the axial end edge 310, ensuring that the axial end edge 310 of the cantilever structure along the X-axis is supported and restricted even at its extended point, thus guaranteeing a certain level of shock resistance and strength for the first sealing member 300 under high-speed impeller operation. In a preferred embodiment, the two sides of the axial end edge 310 can be arc-shaped, resulting in a linear contact point with the sidewalls of the sealing groove 410, thereby effectively reducing friction while ensuring a seal. The top end of the axial end edge 310 may or may not contact the bottom of the sealing groove 410. The top end of the axial end edge 310 may be arc-shaped, so that the contact point with the top end of the sealing groove 410 is linear.

[0073] In this embodiment, the sealing-related relative structures of the first sealing member 300 and the second sealing member 400 can be interchanged. That is, the first sealing member 300 can also be configured as the sealing structure (sealing groove 410) of the second sealing member 400 of the above preferred embodiment, and the second sealing member 400 can be configured as the sealing structure (axial end edge 310) of the first sealing member 300 of the above preferred embodiment.

[0074] like Figure 3 as well as Figures 8-10 As shown, in a preferred embodiment, the second sealing member 400 is connected to the air inlet ring 200 via a vibration damping mechanism 500, which is configured to absorb vibrations in the radial and / or axial (X) directions. The vibration damping mechanism 500 can reduce vibrations in the axial (X) direction and radial runout generated during the operation of the impeller 100. Of course, in other embodiments, while ensuring a tight seal, the first sealing member 300 may also be connected to the front end 101 of the impeller 100 via the vibration damping mechanism 500. The vibration damping mechanism 500 can be any known vibration damping structure.

[0075] like Figures 8-10As shown, in a preferred embodiment, the damping mechanism 500 includes a body component 510 and an elastic component. The two ends of the body component 510 are respectively connected to the first sealing component 300 and the front end 101 of the impeller 100, or the two ends of the body component 510 are respectively connected to the sealing component and the air inlet ring 200. This prevents the first sealing component 300 or the second sealing component 400 from fatigue failure due to vibration, and also prevents interference and jamming between the first sealing component 300 and the second sealing component 400, which could cause greater damage. The elastic component can be any known element that generates elastic force.

[0076] like Figures 8-10 As shown, in a further preferred embodiment, the elastic component includes a linear spring 520 and a disc spring 530. The linear spring 520 is a positive stiffness element with a stiffness coefficient k > 0; the disc spring 530 is a negative stiffness element with a stiffness coefficient k < 0. After the linear spring 520 and the disc spring 530 are vector-combined, within a certain speed range, the stiffness coefficient k of the load and displacement can be made close to 0, thereby minimizing the displacement change of the first sealing component 300 and the second sealing component 400 within the corresponding dynamic stiffness range, isolating the vibration transmitted from the impeller 100 to the inlet ring 200, and ensuring that while reducing airflow leakage during the rotation of the impeller 100, the vibration of the centrifugal fan is minimized. For example, in some embodiments, the stiffness coefficient k of the linear spring 520 is > 0, k = 800~1000 N / m; the stiffness coefficient k of the disc spring 530 is < 0, generally k = -800~-1000 N / m. After vector combination, k is basically equal to 0 within a certain displacement range. Within a certain speed range, such as 1000 to 2000 rpm, the displacement change within the dynamic stiffness range is minimized, the vibration transmitted from the moving impeller 100 to the air inlet ring 200 is isolated, and the vibration of the fan system is minimized while ensuring that the gas does not leak during the impeller rotation.

[0077] like Figures 8-10 As shown, in a further preferred embodiment, a damping washer 540 and a flat washer 550 are sequentially disposed between the linear spring 520 and the disc spring 530. The flat washer 550 provides a flat contact surface, thereby making the contact of the linear spring 520 more stable, and the flat washer 550 can stabilize the coefficient of friction of the support surface. This helps to reduce the seizing phenomenon caused by local contact and improve the reliability of the connection. The damping washer 540 has a good shock absorption effect and can effectively absorb vibration and reduce noise generation.

[0078] like Figures 8-10As shown, in a further preferred embodiment, the main body component has a columnar body 511 and a surrounding wall 512 surrounding the outside of the columnar body 511, forming a surrounding space 513 between the surrounding wall 512 and the columnar body 511. A linear spring 520, a disc spring 530, a damping washer 540, and a flat washer 550 are all sleeved on the columnar body 511, and the disc spring 530, damping washer 540, and flat washer 550 are accommodated within the surrounding space 513. Thus, the disc spring 530, damping washer 540, and flat washer 550 can be limited and protected.

[0079] like Figures 8-10 As shown, in a further preferred embodiment, the connection at at least one end of the body member 510 is restricted to axial movement in the X direction and / or radial movement. This allows the body member 510 to move to a certain extent in the X direction and / or radial direction, thereby enabling the connected first sealing member 300 and / or second sealing member 400 to move to accommodate the fit, thus preventing structural compression and damage caused by misfitting the first sealing member 300 and the second sealing member 400 in the radial and / or X directions. Simultaneously, when the fit stiffness coefficient k is close to 0, the damping mechanism 500 can still be displaced relative to the first sealing member 300 and / or the second sealing member 400 in the radial and / or X directions to accommodate vibrations and greater movement.

[0080] like Figures 3-10 As shown, in a further preferred embodiment, the second sealing member 400 has a movable groove 420 formed on the side facing the air inlet ring 200. A connecting cover 430 covers the movable groove 420. One end of the body member 510 is restricted by the connecting cover 430 within the movable groove 420, allowing for movement in the X-axis direction and radially. The other end of the body member 510 is fixedly connected to the air inlet ring 200. The movable groove 420 provides space for the body member 510 to move, facilitating reduced installation accuracy of the shock-absorbing component. If the movable groove 420 is further configured as an annular shape, it can further provide movement around the X-axis, further reducing the accuracy requirements of the installation position. Figures 8-10 As shown, one end of the main body component 510 has a protrusion 514. The size of the protrusion 514 is smaller than the size of the movable groove 420, allowing it to move within the movable groove 420. The radial dimension of the protrusion 514 is larger than the diameter of the through hole on the columnar body 511 and the connecting cover 430. This allows the protrusion 514 to be blocked by the connecting cover 430, preventing it from leaving the movable groove 420. Furthermore, one end of the columnar body 511 is provided with a threaded portion 515, which allows for a detachable threaded connection with the air inlet ring 200. Multiple shock-absorbing mechanisms 500 and movable grooves, as shown, can be evenly arranged around the body to provide more uniform shock absorption support.

[0081] like Figures 3-10 As shown, in a further preferred embodiment, a sealing groove 410 is provided on the second sealing member 400 or the first sealing member 300, and at least a portion of the corresponding first sealing member 300 or second sealing member 400 mates with the sealing groove 410. The connection position of the shock-absorbing mechanism 500 is aligned with the sealing groove 410 (i.e., in...). Figure 3 (Aligned left and right in the middle). This allows the force acting on the sealing groove 410 in the X direction to be directly borne by the damping mechanism 500, thereby absorbing vibrations in the X direction more directly and avoiding shearing forces on the first sealing member 300 or the second sealing member 400.

[0082] like Figures 3-10 As shown, in a further preferred embodiment, the first blocking member 300 includes a radially extending end edge 320, and the impeller 100 includes a plurality of blades 110. The radial end edge 320 extends radially and connects to the ends of each blade 110. Thus, the radial end edge 320 not only serves as part of the first blocking member 300, but also connects and fixes each blade 110 at the front end 101 of the impeller 100, and the radial end edge 320 can also block part of the airflow.

[0083] like Figures 3-10 As shown, in a further preferred embodiment, the second sealing member 400 has a movable groove 420 on the side facing the air inlet ring 200, which is used to connect with the damping mechanism 500. The second sealing member 400 also has a sealing groove 410 on the side facing the front end 101 of the impeller 100, which is used to cooperate with the first sealing member 300. The air inlet ring 200 has an inner extension section 210 extending towards the impeller 100. The second sealing member 400 is sealed to the inner extension section 210, and the extension lengths of the inner extension section 210 and the sealing groove 410 at least partially overlap in the X-axis direction. This allows the material between the movable groove 420 and the sealing groove 410 of the second sealing member 400 to be supported by the inner extension section 210 of the air inlet ring 200. When the movable groove 420 and the sealing groove 410 are subjected to radial force, damage occurs at the weak point of their connection.

[0084] In summary, the centrifugal fan described in this embodiment can be used in range hoods or other compatible products. Other components of the centrifugal fan can be adjusted according to actual needs.

[0085] This invention eliminates aerodynamic performance loss caused by airflow leakage and improves fan efficiency when various conventional optimization conditions cannot be further optimized.

[0086] While specific embodiments of the present invention have been described above, those skilled in the art should understand that these are merely illustrative examples, and the scope of protection of the present invention is defined by the appended claims. Those skilled in the art can make various changes or modifications to these embodiments without departing from the principles and essence of the present invention, but all such changes and modifications fall within the scope of protection of the present invention.

Claims

1. A centrifugal fan, comprising a volute, an air inlet disposed on the volute, an impeller disposed within the volute, and an air inlet ring connected to the volute, characterized in that, The centrifugal fan further includes a first sealing component and a second sealing component. The first sealing component is connected or indirectly connected to the front end of the impeller; the second sealing component is directly or indirectly fixed to the inner side of the inlet ring. The first and second sealing components extend circumferentially around the axis of the impeller, and are sealed together to block the gap between the inlet ring and the front end of the impeller. The first and second sealing components are in contact with and sealed to each other, and / or the second sealing component and the inlet ring are in contact with and sealed to each other. A sealing groove is provided on the second sealing member or the first sealing member. At least a portion of the first sealing member or the second sealing member mates with the sealing groove. The second sealing member or the first sealing member includes an axial end edge extending along the axial direction. The sealing groove is recessed along the axial direction and is annular in shape. The sidewalls of the sealing groove are attached to both sides of the axial end edge. The first sealing member is connected to the front end of the impeller through a shock-absorbing mechanism, and / or the second sealing member is connected to the air inlet ring through a shock-absorbing mechanism. The shock-absorbing mechanism is configured to absorb vibration in the radial and / or axial directions.

2. The centrifugal fan as described in claim 1, characterized in that, The shock absorption mechanism includes a main body component and an elastic component. The two ends of the main body component are respectively connected to the first sealing component and the front end of the impeller, or the two ends of the main body component are respectively connected to the sealing component and the air inlet ring.

3. The centrifugal fan as described in claim 2, characterized in that, The elastic component includes linear springs and disc springs.

4. The centrifugal fan as described in claim 3, characterized in that, A damping washer and / or a flat washer are sequentially provided between the linear spring and the disc spring.

5. The centrifugal fan as described in claim 4, characterized in that, The main body component has a columnar body and a surrounding wall surrounding the outside of the columnar body, forming a surrounding space between the surrounding wall and the columnar body. The linear spring, the disc spring, the damping pad and / or the flat pad are all sleeved on the columnar body, and the disc spring, the damping pad and / or the flat pad are accommodated within the surrounding space.

6. The centrifugal fan as described in claim 2 or 3, characterized in that, The connection at at least one end of the body component is restricted to being movable in the axial direction and / or radially.

7. The centrifugal fan as described in claim 2, characterized in that, The second sealing member has a movable groove on the side facing the air inlet ring. A connecting cover is provided on the movable groove. One end of the main body member is restricted by the connecting cover to move in the movable groove in the axial direction and the radial direction. The other end of the main body member is fixedly connected to the air inlet ring.

8. The centrifugal fan as described in claim 1, characterized in that, The second sealing member or the first sealing member is provided with a sealing groove, and at least a portion of the corresponding first sealing member or the second sealing member cooperates with the sealing groove. The connection position of the shock absorption mechanism is aligned with the sealing groove.

9. The centrifugal fan as described in claim 1, characterized in that, The first sealing member includes a radially extending end edge, and the impeller includes a plurality of blades, the radially extending end edge being connected to the end of each of the blades.

10. The centrifugal fan according to any one of claims 1-9, characterized in that, The second sealing member has a movable groove on the side facing the air inlet ring, which is used to connect with the shock absorption mechanism. The second sealing member has a sealing groove on the side facing the front end of the impeller, which is used to cooperate with the first sealing member. The air inlet ring has an inner extension section extending toward the impeller. The second sealing member is sealed to the inner extension section. The extension lengths of the inner extension section and the sealing groove at least partially overlap in the direction of the axis.

11. A range hood, characterized in that, It includes the centrifugal fan as described in any one of claims 1-10.

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