Centrifugal fan and range hood comprising same

Abstract

The invention discloses a centrifugal fan and a range hood comprising the same. The centrifugal fan comprises a volute, an air inlet formed in the volute, an impeller arranged in the volute and an air inlet ring connected to the volute, the centrifugal fan further comprises a first plugging component and a second plugging component, and the first plugging component is connected or indirectly connected to the front end of the impeller; the second plugging component is directly or indirectly fixed on the inner side of the air inlet ring; the first blocking component and the second blocking component annularly extend in the axis direction of the impeller, and the first blocking component and the second blocking component are connected in a sealed mode and block a notch between the air inlet ring and the front end of the impeller. According to the method, aerodynamic performance loss caused by airflow leakage is eliminated, and the efficiency of the fan is improved under the condition that further optimization cannot be carried out under various conventional optimization conditions.

Description

Technical Field

[0001] The invention relates to a centrifugal fan and a range hood comprising the same. Background Art

[0002] Centrifugal fans are widely used in various fields. For example, in the field of range hoods, oil smoke is usually sucked by centrifugal fans. For example, the centrifugal fan disclosed in the Chinese patent application publication CN219691821U includes a volute and an impeller arranged in the volute. The impeller rotates to make the gas flow from the outside of the volute into the air inlet and into the volute. The air inlet ring plays a role of guiding the wind at the air inlet.

[0003] The advantages of current centrifugal fans are high static pressure and low noise. However, their aerodynamic efficiency is relatively low in impeller machinery. For example, the aerodynamic efficiency of a forward multi-blade fan is generally 55% to 58%, which is relatively low. Conventional optimization of blade parameters, matching of volute profile design, or optimization of inlet and outlet resistance has its limits, and there is little room for optimization, resulting in the inability to further improve aerodynamic efficiency. Summary of the invention

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

[0005] The present invention solves the above technical problems through the following technical solutions:

[0006] A centrifugal fan comprises a volute, an air inlet arranged on the volute, an impeller arranged in the volute and an air inlet ring connected to the volute, the centrifugal fan also comprises 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 in a ring shape around the axial direction of the impeller, and the first sealing member and the second sealing member are sealingly connected and seal the gap between the air inlet ring and the front end of the impeller.

[0007] In this solution, by sealing the air inlet ring and the front end of the impeller, the air flow coming out from the peripheral side of the impeller can no longer leak through the gap between the air inlet ring and the front end of the impeller, thereby avoiding the existence of secondary flow between the front disk and the air inlet ring of the centrifugal fan, eliminating the loss of aerodynamic performance caused by air flow leakage, and achieving an improvement in fan efficiency when various conventional optimization conditions cannot be further optimized.

[0008] Preferably, the first blocking member and the second blocking member are not in contact, wherein the first blocking member and the second blocking member are spaced apart along the axial direction and their projections along the axis at least partially overlap. The difficulty of airflow outflow can be increased by overlapping in the axial direction, wherein most of the airflow outflowing from the second blocking member is directly blocked by the second blocking member protruding due to the overlap, and thus does not flow out, while the remaining small part of the airflow has a slow flow rate and a small outflow amount due to the circuitous interval between the first blocking member and the second blocking member, thereby still being able to significantly prevent considerable airflow leakage as a whole, thereby ensuring the improvement of the fan efficiency. In addition, the non-contacting first blocking member and the second blocking member will not cause motion interference, thereby avoiding wear.

[0009] Preferably, the first blocking member and the second blocking member are in contact and sealed with each other, and / or the second blocking member and the air inlet ring are in contact and sealed with each other. The second blocking member can completely prevent any airflow from flowing out through the gap between the second blocking member and the first blocking member, and the gap between the second blocking member and the air inlet ring, by sealing with the first blocking member and the air inlet ring respectively, thereby maximizing the efficiency of the fan.

[0010] Preferably, a sealing groove is provided on the second blocking member or the first blocking member, and at least a portion of the corresponding first blocking member or the second blocking member cooperates with the sealing groove. The sealing groove seals the first blocking member or the second blocking member more perfectly, and a good sealing effect can be obtained through the sealing of the sealing groove without the need for additional auxiliary sealing media.

[0011] Preferably, 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, and the side walls of the sealing groove are fitted on both sides of the axial end edge. The axial end edge can thus rotate in the annular sealing groove, so that the relative movement between the first sealing member and the second sealing member can be guaranteed while sealing. The side walls of the sealing groove also support the axial end edge, so that the axial end edge of the cantilever structure in the axial direction can be supported and restricted at the far point of extension, thereby ensuring a certain seismic resistance and strength of the first sealing member under high-speed operation of the impeller.

[0012] Preferably, the first blocking member is connected to the front end of the impeller through a shock absorbing mechanism, and / or the second blocking member is connected to the air inlet ring through a shock absorbing mechanism, and the shock absorbing mechanism is configured to absorb vibration in the radial direction and / or the axial direction. The shock absorbing mechanism can reduce the axial vibration and radial runout generated when the impeller is running.

[0013] Preferably, the shock absorbing mechanism includes a main body component and an elastic component, and 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, so as to avoid fatigue failure of the first sealing component or the second sealing component due to vibration, and also avoid interference and jamming between the first sealing component and the second sealing component to cause greater damage.

[0014] Preferably, the elastic member includes a linear spring and a disc spring. The linear spring is a positive stiffness element, and the stiffness coefficient k>0; the disc spring is a negative stiffness element, and the stiffness coefficient k<0. After the linear spring and the disc spring are vector-synthesized, within a certain speed range, the stiffness coefficient k of the load and displacement can be close to 0, so that the displacement change of the first blocking member and the second blocking member within the corresponding dynamic stiffness range is minimized, the vibration transmitted from the impeller to the air inlet ring is cut off, and the vibration of the centrifugal fan is minimized while reducing airflow leakage during the rotation of the impeller.

[0015] Preferably, a damping washer and / or a flat washer are arranged in sequence between the linear spring and the disc spring. The flat washer can provide a flat contact surface so that the contact of the linear spring is more stable, and the flat washer can stabilize the friction coefficient of the supporting surface. This helps to reduce the sticking phenomenon caused by local contact and improve the reliability of the connection. The damping washer has a good shockproof effect and can effectively absorb vibration and reduce noise generation.

[0016] Preferably, the main body component has a columnar body and a surrounding wall surrounding the outer side of the columnar body, a surrounding space is formed 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 in the surrounding space. Thus, the disc spring, the damping washer and / or the flat washer can be limited and protected.

[0017] Preferably, the connection of at least one end of the main body member is limited to be movable in the axial direction and / or the radial direction. In this way, the main body member can be moved in the axial direction and / or the radial direction to a certain extent, so that the first blocking member and / or the second blocking member connected thereto can be moved to a certain extent to adapt to the fit, thereby avoiding the compression and damage of the structure caused by the fit error of the first blocking member and the second blocking member in the radial and / or axial direction. At the same time, when the fit stiffness coefficient k is close to 0, the shock absorbing mechanism as a whole can still be displaced relative to the first blocking member and / or the second blocking member in the radial and / or axial direction to adapt to vibration and larger movements.

[0018] Preferably, a moving groove is formed on the side of the second blocking member facing the air inlet ring, and the moving groove is covered with a connection cover, one end of the main body member is restricted by the connection cover to move in the moving groove in the axial direction and the radial direction, and the other end of the main body member is fixedly connected to the air inlet ring. The moving groove provides a movable space for the main body member, which is convenient for reducing the installation accuracy of the shock-absorbing member. When the moving groove is further set to be annular, it can further provide movement around the axial direction, further reducing the accuracy requirements of the installation position.

[0019] Preferably, a sealing groove is provided on the second blocking member or the first blocking member, at least a portion of the corresponding first blocking member or the second blocking member cooperates with the sealing groove, and the connection position of the shock absorbing mechanism is aligned with the sealing groove, so that the force acting on the axial direction of the sealing groove can be directly borne by the shock absorbing mechanism, thereby more directly absorbing the vibration in the axial direction and avoiding the generation of shear force on the first blocking member or the second blocking member.

[0020] Preferably, the first blocking member includes a radial end edge extending along the radial direction, the impeller includes a plurality of blades, and the radial end edge extends radially and is connected to the end of each blade. Thus, the radial end edge not only serves as a part of the first blocking member, but also plays a role in connecting and fixing each blade at the front end of the impeller, and the radial end edge can also block part of the airflow from flowing out.

[0021] Preferably, a movable groove is provided on one side of the second blocking member facing the air inlet ring, and the movable groove is used to connect with the shock absorbing mechanism; a sealing groove is provided on one side of the second blocking member facing the front end of the impeller, and the sealing groove is used to cooperate with the first blocking member; the air inlet ring has an inner extension section extending toward the impeller, and the second blocking member is sealed and cooperates with the inner extension section, and the extension lengths of the inner extension section and the sealing groove at least partially overlap in the axial direction. In this way, the material between the movable groove and the sealing groove of the second blocking member can be supported by the inner extension section of the air inlet ring, and the movable groove and the sealing groove are damaged at the weak connection between the two when subjected to radial force.

[0022] A range hood comprises the centrifugal fan.

[0023] The positive and progressive effects of the present invention are: eliminating the loss of aerodynamic performance caused by airflow leakage, and achieving an improvement in fan efficiency when various conventional optimization conditions cannot be further optimized. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1The figure is a schematic diagram of the three-dimensional structure of a centrifugal fan according to a preferred embodiment of the present invention.

[0025] Figure 2 The figure is a schematic cross-sectional structure diagram of a centrifugal fan according to a preferred embodiment of the present invention.

[0026] Figure 3 for Figure 2 A magnified schematic diagram of part A in FIG.

[0027] Figure 4 The figure is a schematic diagram of the exploded structure of a centrifugal fan according to a preferred embodiment of the present invention.

[0028] Figure 5 It is a three-dimensional schematic diagram of the first blocking member according to a preferred embodiment of the present invention.

[0029] Figure 6 It is a three-dimensional structural schematic diagram of the second blocking component of a preferred embodiment of the present invention.

[0030] Figure 7 Another schematic diagram of the three-dimensional structure of the second blocking member according to a preferred embodiment of the present invention.

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

[0032] Fig. 9 It is a schematic cross-sectional structure diagram of a shock absorbing mechanism according to a preferred embodiment of the present invention.

[0033] Fig.10 Schematic diagram of the exploded structure of the shock absorbing mechanism of a preferred embodiment of the present invention.

[0034] Description of Reference Numerals

[0035] Impeller 100

[0036] Front-end 101

[0037] Blade 110

[0038] Air inlet ring 200

[0039] Inner extension section 210

[0040] First blocking member 300

[0041] Axial edge 310

[0042] Radial edge 320

[0043] Second blocking member 400

[0044] Sealing groove 410

[0045] Mobile groove 420

[0046] Connection cover 430

[0047] Shock absorber 500

[0048] Main body member 510

[0049] Column body 511

[0050] Surrounding wall 512

[0051] Surrounding Space 513

[0052] Protrusion 514

[0053] Threaded portion 515

[0054] Linear Spring 520

[0055] Disc spring 530

[0056] Damping gasket 540

[0057] Flat Washer 550

[0058] Volute 600

[0059] Air Inlet 610

[0060] Gap 700

[0061] Axis X

[0062] Overlap distance B DETAILED DESCRIPTION

[0063] The present invention is further described below by way of examples, but the present invention is not limited to the scope of the examples.

[0064] like Figure 1-Figure 10 As shown, the present embodiment discloses a centrifugal fan, comprising a volute 600, an air inlet 610 arranged on the volute 600, an impeller 100 arranged in the volute 600, and an air inlet ring 200 connected to the volute 600, the centrifugal fan also comprises a first blocking member 300 and a second blocking member 400, wherein the first blocking member 300 is connected or indirectly connected to the front end 101 of the impeller 100; the second blocking member 400 is directly or indirectly fixed to the inner side of the air inlet ring 200; the first blocking member 300 and the second blocking member 400 extend in a ring shape around the axis X direction of the impeller 100, and the first blocking member 300 and the second blocking member 400 are sealed and connected to block the gap 700 between the air inlet ring 200 and the front end 101 of the impeller 100.

[0065] like Figure 1As shown, the air inlet 610 of the volute 600 in this embodiment is a circular opening, the air inlet ring 200 is connected to the volute 600, and the air inlet ring 200 has a guiding surface shape, so that the incoming air enters the impeller 100 in the air inlet 610 through the surface of the air inlet ring 200, such as an arc shape. The axis X is usually the rotation axis of the impeller 100. The relative connection relationship 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, the air inlet ring 200 and the front end 101 of the impeller 100 in this embodiment are in the direction of the axis X ( 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 there is no interference between the air inlet ring 200 and the impeller 100. The distance between the air inlet ring 200 and the front end 101 of the impeller 100 in the axis X direction forms a gap 700. When the gap 700 is not closed, for example Figure 3 The airflow in the left and right directions (radial direction of the impeller 100) can flow freely. The gap 700 is essentially an annular space. After the air inlet of the centrifugal fan enters the impeller 100, part of the airflow will flow along the direction such as Figure 2 and Figure 3 This part of the airflow flows out from the gap between the blades 110 on the outer peripheral side 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 blocking member 300 and the second blocking member 400 are not provided to block the gap 700, the air flows 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] The first blocking member 300 and the second blocking member 400 of this embodiment can completely ensure the airtight seal of the gap 700, that is, the first blocking member 300 and the second blocking member 400 adopt an interference fit so that there is no gap between them. It can also be to complete the blocking of most of the gap 700, and only a small amount of gas escapes from the gap between the first blocking member 300 and the second blocking member 400, that is, the first blocking member 300 and the second blocking member 400 adopt a transition fit or a close fit between the two or other methods to block the escape of the airflow to achieve a rough seal.

[0068] In the present 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 peripheral side 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, thereby avoiding the existence of secondary flow between the front disk and the air inlet ring 200 of the centrifugal fan, eliminating the loss of aerodynamic performance caused by airflow leakage, and achieving an improvement in the efficiency of the fan when various conventional optimization conditions cannot be further optimized.

[0069] In some optional embodiments, the first blocking member 300 and the second blocking member 400 are not in contact, wherein the first blocking member 300 and the second blocking member 400 are spaced apart along the axis X direction and the projections along the axis X at least partially overlap. The difficulty of airflow outflow can be increased by overlapping in the axis X direction, wherein most of the airflow outflowing from the second blocking member 400 is directly blocked by the second blocking member 400 protruding due to the overlap, so that it does not flow out, and the remaining small part of the airflow has a slow flow rate and a small outflow due to the circuitous interval between the first blocking member 300 and the second blocking member 400, thereby still being able to significantly prevent the leakage of considerable airflow as a whole, ensuring the improvement of the fan efficiency. In addition, the non-contacting first blocking member 300 and the second blocking member 400 will not produce motion interference, avoiding wear.

[0070] like Figure 3 As shown, in a preferred embodiment, the first blocking member 300 and the second blocking member 400 are in contact and sealed with each other, and / or the second blocking member 400 and the air inlet ring 200 are in contact and sealed with each other. The second blocking member 400 can completely prevent any airflow from flowing out through the gap between the second blocking member 400 and the first blocking member 300, and the gap between the second blocking member 400 and the air inlet ring 200, by sealing with the first blocking member 300 and the air inlet ring 200 respectively, thereby maximizing the efficiency of the fan.

[0071] like Figure 3-Figure 7 As shown, in a further preferred embodiment, a sealing groove 410 is provided on the second blocking member 400, and at least a portion of the corresponding first blocking member 300 cooperates with the sealing groove 410. The sealing groove 410 seals the first blocking member 300 or the second blocking member 400 more perfectly, and a good sealing effect can be obtained through the sealing of the sealing groove 410 without the need for additional auxiliary sealing media.

[0072] like Figure 3-Figure 7As shown, in a further preferred embodiment, the first blocking member 300 includes an axial end edge 310 extending along the axis X direction, and the sealing groove 410 is recessed along the axial direction and is annular in shape, and the side walls of the sealing groove 410 are attached to both sides of the axial end edge 310. The axial end edge 310 can thus rotate in the annular sealing groove 410, so that the relative movement between the first blocking member 300 and the second blocking member 400 can be guaranteed while sealing. The side wall of the sealing groove 410 also has a supporting effect on the axial end edge 310, so that the axial end edge 310 of the cantilever structure in the axis X direction can also be supported and restricted at the far point of extension, thereby ensuring a certain anti-seismic performance and strength of the first blocking member 300 under high-speed operation of the impeller 100. In a preferred manner, both sides of the axial end edge 310 can be in the shape of an arc, so that the contact point with the side wall of the sealing groove 410 is linear, thereby effectively reducing friction while ensuring sealing. The top of the axial end edge 310 may or may not contact the groove bottom of the sealing groove 410. The top of the axial end edge 310 may be arc-shaped, so that the contact point with the top of the sealing groove 410 may also be 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 to have the sealing structure (sealing groove 410) of the second sealing member 400 of the above-mentioned preferred embodiment, and the second sealing member 400 can be configured to have the sealing structure (axial end edge 310) of the first sealing member 300 of the above-mentioned preferred embodiment.

[0074] like Figure 3 as well as Figure 8-Figure 10 As shown, in a preferred embodiment, the second blocking member 400 is connected to the air inlet ring 200 through a shock absorbing mechanism 500, and the shock absorbing mechanism 500 is configured to absorb vibration in the radial direction and / or the axis X direction. The shock absorbing mechanism 500 can reduce the vibration in the axis X direction and the radial runout generated when the impeller 100 is running. Of course, in other embodiments, the first blocking member 300 can also be allowed to be connected to the front end 101 of the impeller 100 through the shock absorbing mechanism 500 while ensuring sealing. The shock absorbing mechanism 500 can be various known shock absorbing structures.

[0075] like Figure 8-Figure 10As shown, in a preferred embodiment, the shock absorbing mechanism 500 includes a body component 510 and an elastic component, and the two ends of the body component 510 are respectively connected to the first blocking 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 blocking component and the air inlet ring 200, so as to avoid fatigue failure of the first blocking component 300 or the second blocking component 400 due to vibration, and also avoid interference and jamming between the first blocking component 300 and the second blocking component 400 to cause greater damage. The elastic component can be various known elements that generate elastic force.

[0076] like Figure 8-Figure 10 As shown, in a further preferred embodiment, the elastic member includes a linear spring 520 and a disc spring 530. The linear spring 520 is a positive stiffness element, and the stiffness coefficient k>0; the disc spring 530 is a negative stiffness element, and the stiffness coefficient k<0. After the linear spring 520 and the disc spring 530 are vector-synthesized, within a certain speed range, the stiffness coefficient k of the load and displacement can be close to 0, so that the displacement change of the first blocking member 300 and the second blocking member 400 in the corresponding dynamic stiffness range is minimized, the vibration transmitted from the impeller 100 to the air inlet ring 200 is cut off, and the vibration of the centrifugal fan is minimized while reducing the airflow leakage during the rotation of the impeller 100. For example, in some embodiments, the stiffness coefficient k of the linear spring 520 is>0, k=800~1000N / m; the stiffness coefficient k of the disc spring 530 is<0, generally k=-800~-1000N / m, and after vector synthesis, k is basically equal to 0 within a certain displacement range. In a certain speed range, such as 1000-2000 rpm, the displacement change in the dynamic stiffness range is minimized, the vibration transmitted from the impeller 100 to the air inlet ring 200 is blocked, and the gas is not leaked during the rotation of the impeller, while the vibration of the fan system is minimized.

[0077] like Figure 8-Figure 10 As shown, in a further preferred embodiment, a damping washer 540 and a flat washer 550 are sequentially arranged between the linear spring 520 and the disc spring 530. The flat washer 550 can provide a flat contact surface so that the contact of the linear spring 520 is more stable, and the flat washer 550 can stabilize the friction coefficient of the supporting surface. This helps to reduce the sticking phenomenon caused by local contact and improve the reliability of the connection. The damping washer 540 has a good shockproof effect and can effectively absorb vibration and reduce noise generation.

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

[0079] like Figure 8-Figure 10 As shown, in a further preferred embodiment, the connection of at least one end of the main body member 510 is limited to be movable in the axis X direction and / or radial direction. Thus, the main body member 510 can be moved in the axis X direction and / or radial direction to a certain extent, so that the first blocking member 300 and / or the second blocking member 400 connected thereto can be moved to a certain extent to adapt to the fit, thereby avoiding the first blocking member 300 and the second blocking member 400 from being compressed and damaged due to the fit error in the radial direction and / or the axis X direction. At the same time, when the fit stiffness coefficient k is close to 0, the damping mechanism 500 can still be displaced relative to the first blocking member 300 and / or the second blocking member 400 in the radial direction and / or the axis X direction as a whole to adapt to vibration and greater movement.

[0080] like Figure 3-Figure 10 As shown, in a further preferred embodiment, a movable groove 420 is formed on the side of the second blocking member 400 facing the air inlet ring 200, and the movable groove 420 is covered with a connection cover 430. One end of the main body member 510 is restricted by the connection cover 430 in the movable groove 420 to move in the axis X direction and radial direction, and the other end of the main body member 510 is fixedly connected to the air inlet ring 200. The movable groove 420 provides a movable space for the main body member 510, which is convenient for reducing the installation accuracy of the shock-absorbing member. When the movable groove 420 is further set to be annular, it can further provide movement around the axis X direction, further reducing the accuracy requirements of the installation position. Figure 8-Figure 10 As shown, one end of the main body member 510 has a protrusion 514, and the size of the protrusion 514 is smaller than the size of the moving groove 420 so that it can move in the moving groove 420. The radial size of the protrusion 514 is larger than the aperture of the through hole on the columnar body 511 and the connection cover 430. As a result, the protrusion 514 can be blocked by the connection cover 430 and cannot leave the moving groove 420. In addition, one end of the columnar body 511 is provided with a threaded portion 515, and the threaded portion 515 can be connected to the air inlet ring 200 through a detachable and fixed connection of the thread. The shock absorbing mechanism 500 and the moving groove can be multiple as shown in the figure, evenly arranged around, so as to provide more uniform shock absorbing support.

[0081] like Figure 3-Figure 10 As shown, in a further preferred embodiment, a sealing groove 410 is provided on the second blocking member 400 or the first blocking member 300, at least a portion of the corresponding first blocking member 300 or the second blocking member 400 cooperates with the sealing groove 410, and the connection position of the shock absorbing mechanism 500 is aligned with the sealing groove 410 (i.e., Figure 3 Thus, the force acting on the sealing groove 410 in the axis X direction can be directly borne by the shock absorbing mechanism 500, so that the vibration in the axis X direction can be more directly absorbed and the shear force on the first blocking member 300 or the second blocking member 400 can be avoided.

[0082] like Figure 3-Figure 10 As shown, in a further preferred embodiment, the first blocking member 300 includes a radial end edge 320 extending in the radial direction, the impeller 100 includes a plurality of blades 110, and the radial end edge 320 extends radially and is connected to the end of each blade 110. Thus, the radial end edge 320 not only serves as a part of the first blocking member 300, but also plays a role in connecting and fixing 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 from flowing out.

[0083] like Figure 3-Figure 10 As shown, in a further preferred embodiment, a movable groove 420 is provided on one side of the second blocking member 400 facing the air inlet ring 200, and the movable groove 420 is used to connect with the damping mechanism 500. A sealing groove 410 is provided on one side of the second blocking member 400 facing the front end 101 of the impeller 100, and the sealing groove 410 is used to cooperate with the first blocking member 300. The air inlet ring 200 has an inner extension section 210 extending toward the impeller 100, and the second blocking member 400 is sealed and matched with 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 direction of the axis X. As a result, the material between the movable groove 420 and the sealing groove 410 of the second blocking member 400 can be supported by the inner extension section 210 of the air inlet ring 200, and the movable groove 420 and the sealing groove 410 are damaged at the weak connection between the two when the radial force acts on them.

[0084] The centrifugal fan of the present embodiment described above can be applied to a range hood or other adaptable products. Other components of the centrifugal fan can be adjusted according to actual needs.

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

[0086] Although the specific embodiments of the present invention are described above, it should be understood by those skilled in the art that this is only for illustration and the protection scope of the present invention is defined by the appended claims. Those skilled in the art may make various changes or modifications to these embodiments without departing from the principles and essence of the present invention, but these changes and modifications all fall within the protection scope of the present invention.

Claims

1. A centrifugal fan, comprising a volute, an air inlet disposed on the volute, an impeller disposed in the volute, and an air inlet ring connected to the volute, characterized in that: 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 in a ring shape around the axial direction of the impeller, and the first sealing member and the second sealing member are sealingly connected and seal the gap between the air inlet ring and the front end of the impeller.

2. The centrifugal fan according to claim 1, characterized in that: The first blocking member and the second blocking member are not in contact with each other, wherein the first blocking member and the second blocking member are spaced apart along the axis direction and their projections along the axis at least partially overlap.

3. The centrifugal fan according to claim 1, characterized in that: The first blocking member and the second blocking member are in contact with and sealed to each other, and / or the second blocking member and the air inlet ring are in contact with and sealed to each other.

4. The centrifugal fan according to claim 3, characterized in that: The second blocking member or the first blocking member is provided with a sealing groove, and at least a portion of the corresponding first blocking member or the second blocking member cooperates with the sealing groove.

5. The centrifugal fan according to claim 4, characterized in that: The second blocking member or the first blocking member includes an axial end edge extending along the axial direction, the sealing groove is recessed along the axial direction and has a ring shape, and the side walls of the sealing groove are attached to both sides of the axial end edge.

6. The centrifugal fan according to claim 3, characterized in that: The first blocking member is connected to the front end of the impeller through a shock absorbing mechanism, and / or the second blocking member is connected to the air inlet ring through a shock absorbing mechanism, and the shock absorbing mechanism is configured to absorb vibration in the radial direction and / or the axial direction.

7. The centrifugal fan according to claim 6, characterized in that: The shock absorbing mechanism comprises a main body component and an elastic component, and two ends of the main body component are respectively connected to the first blocking component and the front end of the impeller, or two ends of the main body component are respectively connected to the blocking component and the air inlet ring.

8. The centrifugal fan according to claim 7, characterized in that: The elastic member includes a linear spring and a disc spring.

9. The centrifugal fan according to claim 8, characterized in that: A damping washer and / or a flat washer are arranged in sequence between the linear spring and the disc spring.

10. The centrifugal fan according to claim 9, characterized in that: The main body component has a cylindrical body and a surrounding wall surrounding the outside of the cylindrical body, a surrounding space is formed between the surrounding wall and the cylindrical body, the linear spring, the disc spring, the damping gasket and / or the flat gasket are all mounted on the cylindrical body, and the disc spring, the damping gasket and / or the flat gasket are accommodated in the surrounding space.

11. The centrifugal fan according to claim 7 or 8, characterized in that: The connection of at least one end of the body member is restricted to be movable in the axial direction and / or radial direction.

12. The centrifugal fan according to claim 7, characterized in that: A movable groove is formed on the side of the second sealing component facing the air inlet ring, and the movable groove is covered with a connecting cover. One end of the main body component is restricted by the connecting cover to move in the movable groove in the axial direction and the radial direction, and the other end of the main body component is fixedly connected to the air inlet ring.

13. The centrifugal fan according to claim 6, characterized in that: The second blocking member or the first blocking member is provided with a sealing groove, at least a portion of the corresponding first blocking member or the second blocking member cooperates with the sealing groove, and the connection position of the shock absorbing mechanism is aligned with the sealing groove.

14. The centrifugal fan according to claim 1, characterized in that: The first blocking member includes a radial end edge extending in the radial direction, the impeller includes a plurality of blades, and the radial end edge extends in the radial direction and is connected to the end of each of the blades.

15. The centrifugal fan according to any one of claims 1 to 14, characterized in that: A movable groove is provided on the side of the second sealing member facing the air inlet ring, and the movable groove is used to be connected to the shock absorbing mechanism. A sealing groove is provided on the side of the second sealing member facing the front end of the impeller, and the sealing groove is used to cooperate with the first sealing member. The air inlet ring has an inner extension section extending toward the impeller, and the second sealing member is sealed and cooperated with 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.

16. A range hood, characterized in that: It comprises the centrifugal fan as described in any one of claims 1-15.

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