Self-cleaning fan and range hood

Abstract

The present invention relates to a self-cleaning fan and a range hood, which can achieve the global cleaning of the impeller and obtain a better cleaning effect. The self-cleaning fan includes a fan main body and a cleaning device. The fan main body includes a volute and an impeller rotatably arranged in the volute. A plurality of blades are arranged circumferentially on the impeller. The cleaning device includes a cleaning medium supply member rotatably arranged relative to the volute. The cleaning medium supply member has spray holes for spraying the cleaning medium. When the self-cleaning fan performs self-cleaning, the impeller and / or the cleaning medium supply member rotates at a variable speed relative to the volute, and the cleaning medium supply member is used to spray the cleaning medium onto the blades to form a plurality of impact starting points arranged axially on the surface of each blade; wherein the distance between two axially adjacent impact starting points on each blade is greater than or equal to the inner diameter size of the spray hole and less than or equal to 10 times the inner diameter size of the spray hole.

Description

[0001] This application claims priority to the Chinese patent application filed with the China Patent Office on November 1, 2021, with application number 202111284408.2 and application name “Fan cleaning device and range hood for range hood”, the entire contents of which are incorporated by reference into this application. Technical Field

[0002] The invention relates to the technical field of kitchen equipment, in particular to a self-cleaning fan and a range hood. Background Art

[0003] With the continuous advancement of range hood self-cleaning technology, steam cleaning or water cleaning has been widely used in the field of range hood self-cleaning. The basic principle is that the steam generator generates steam or the water pump pumps water, and the steam or water is transported to the nozzle at the end of the nozzle. The steam or water is quickly ejected from the nozzle to flush the impeller and volute for cleaning.

[0004] At present, fixed holes are generally opened on the nozzle, and the number of holes is generally more than 3, but this cleaning method has the following shortcomings: first, during cleaning, steam or water is sprayed out from a fixed nozzle. Since there are a limited number of nozzles, the flushing force at the intervals between the nozzles is very weak, and the cleaning effect is not good; second, due to the large number of holes and the power of the steam generator or pump is constant, the steam pressure or water pressure coming out of the nozzle is correspondingly low and unstable, resulting in a poor cleaning effect.

[0005] In order to increase the flushing force, improve the cleaning effect and achieve comprehensive cleaning, the applicant's prior application, the invention patent with application number CN201711480573.9 (publication number CN109990332A) "A cleaning device for the fan system of a range hood" and the utility model patent with patent application number CN201920819655.X (publication number CN210197396U) "A range hood with self-cleaning function" both proposed a design idea of comprehensively cleaning the impeller by moving the cleaning medium supply part to improve the cleaning effect.

[0006] However, the first solution mentioned above has to open a long strip of clearance hole on the volute extending along the moving direction of the cleaning medium supply part, which requires a large modification to the original structure of the fan and is likely to affect the performance of the fan. If an additional shielding part is provided, there is a problem that the sticky grease will stick to the shielding part after long-term use, causing it to be unable to open or close tightly. Although the second solution mentioned above does not require a larger clearance hole, the horizontal feed type cleaning medium supply part thereof needs to occupy a large amount of end side space, and the size of existing products can hardly support such a large space. Summary of the invention

[0007] One advantage of the present invention is to provide a self-cleaning fan and a range hood, which can achieve the full-range cleaning of the impeller and obtain a good cleaning effect.

[0008] Another advantage of the present invention is to provide a self-cleaning fan and a range hood. In one embodiment of the present invention, the self-cleaning fan can improve the cleaning efficiency while achieving full-range cleaning, which helps to save water resources.

[0009] Another advantage of the present invention is to provide a self-cleaning fan and a range hood. To achieve the above object, expensive materials or complex structures are not required in the present invention. Therefore, the present invention successfully and effectively provides a solution, not only providing a simple self-cleaning fan and a range hood, but also increasing the practicability and reliability of the self-cleaning fan and the range hood.

[0010] To achieve at least one of the above advantages or other advantages and objects of the present invention, the present invention provides a self-cleaning fan, comprising:

[0011] A fan main body, the fan main body includes a volute and an impeller rotatably arranged in the volute, and a plurality of blades are arranged in the circumferential direction of the impeller; and

[0012] A cleaning device, the cleaning device includes a cleaning medium supply member rotatably arranged relative to the volute, the cleaning medium supply member has a spray hole for spraying a cleaning medium, when the self-cleaning fan performs self-cleaning, the impeller and / or the cleaning medium supply member rotate at a variable speed relative to the volute, and the cleaning medium supply member is used for spraying the cleaning medium onto the blades to form a plurality of impact starting points arranged axially on the surface of each blade;

[0013] Wherein the distance between two adjacent impact starting points axially on each blade is greater than or equal to the inner diameter size of the spray hole and less than or equal to 10 times the inner diameter size of the spray hole. With such a setting, the two adjacent impact areas on each blade will not overlap too much to avoid wasting water resources, nor will there be a large gap, ensuring that partial overlap between adjacent sputtering areas is achieved to realize full-range cleaning in the true sense.

[0014] According to an embodiment of the present application, the distance between two adjacent impact starting points axially on each blade is less than or equal to 2 times the inner diameter size of the spray hole. With such a setting, the overlapping range between two adjacent sputtering areas is appropriately increased, which helps to improve the cleaning effect.

[0015] According to an embodiment of the present application, the distance between two adjacent impact starting points on each blade in the axial direction is greater than or equal to 1.2 times the inner diameter of the spray hole. With such a setting, overlap between adjacent impact regions 2201A can be avoided, which helps to further save water resources.

[0016] According to an embodiment of the present application, the impact starting points on each blade are evenly distributed along the axial direction of the impeller, which helps to improve the consistency of the cleaning effect.

[0017] According to an embodiment of the present application, the rotation axis of the cleaning medium supply member is skew perpendicular to the central axis of the impeller.

[0018] According to an embodiment of the present application, when the self-cleaning fan performs self-cleaning, the impeller rotates at a constant speed relative to the volute, and the cleaning medium supply member rotates at a variable speed relative to the volute.

[0019] According to an embodiment of the present application, the angular velocity ω of the cleaning medium supply member and the rotational speed n of the impeller satisfy the relationship: ω = (nPcos 2 θ) / h; where: P is the cleaning coefficient; θ is the rotation angle of the cleaning medium supply member; h is the vertical spraying distance between the rotation axis of the cleaning medium supply member and the blade to be cleaned.

[0020] According to an embodiment of the present application, when the self-cleaning fan performs self-cleaning, the cleaning medium supply member rotates at a constant speed relative to the volute, and the impeller rotates at a variable speed relative to the volute.

[0021] According to an embodiment of the present application, the rotational speed n of the impeller and the angular velocity ω of the cleaning medium supply member satisfy the relationship: n = (ωr 2 ) / (hP); where: P is the cleaning coefficient; r and h are the inclined spraying distance and the vertical spraying distance between the rotation axis of the cleaning medium supply member and the blade to be cleaned, respectively.

[0022] On the other hand, the present application further provides a range hood, including:

[0023] A housing; and

[0024] The self-cleaning fan as described in any one of the above, and the fan body of the self-cleaning fan is disposed within the housing.

[0025] In summary, the self-cleaning fan of the present application can make the distance between two adjacent impact starting points on each blade in the axial direction greater than or equal to the inner diameter of the spray hole and less than or equal to 10 times the inner diameter of the spray hole by rotating the impeller and / or the cleaning medium supply member at variable speeds. This can not only prevent excessive overlap between adjacent impact areas and avoid waste of water resources, but also ensure that there is no large gap between adjacent impact areas, ensuring partial overlap between adjacent sputtering areas to achieve true full-range cleaning. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] Figure 1 Schematic perspective view of the three-dimensional structure of Embodiment 1 of the range hood of the present invention;

[0027] Figure 2 is Figure 1 Schematic perspective view after omitting the housing (the cleaning medium supply member is in the initial position);

[0028] Figure 3 is Figure 2 Longitudinal sectional view after omitting the water tank, steam generator and water receiving box in ;

[0029] Figure 4 is Figure 3 Left view after omitting the volute and drive device in ;

[0030] Figure 5 is Figure 4 Left view after the cleaning medium supply member rotates to the middle position in ;

[0031] Figure 6 is Figure 5 Left view after the cleaning medium supply member rotates to the end position in ;

[0032] Figure 7 is Figure 3 Left view after the cleaning medium supply member rotates to the middle plate position when the fan in is a double-inlet fan;

[0033] Figure 8 is Figure 2 Schematic diagram of the relative position between the cleaning medium supply member and the blade during the rotation process in ;

[0034] Figure 9 Flowchart of the self-cleaning prompt of the range hood in Embodiment 1 of the present invention;

[0035] Figure 10 Flowchart of the full-range cleaning of the range hood in Embodiment 1 of the present invention (with time as the sampling interval);

[0036] Figure 11Flow chart of the overall cleaning of the range hood in Embodiment 1 of the present invention (taking the number of steps as the sampling interval);

[0037] Figure 12 Flow chart of the oil-stained area collection of the range hood in Embodiment 1 of the present invention;

[0038] Figure 13 Longitudinal sectional view of the fan, cleaning medium supply member and driving device of the range hood in Embodiment 2 of the present invention in the non-working state;

[0039] Figure 14 Schematic perspective view of the fan, cleaning medium supply member and driving device of the range hood in Embodiment 3 of the present invention in the non-working state;

[0040] Figure 15 Longitudinal sectional view of the fan, cleaning medium supply member and driving device of the range hood in Embodiment 3 of the present invention in the working state;

[0041] Figure 16 Longitudinal sectional view of the fan, cleaning medium supply member and driving device of the range hood in Embodiment 4 of the present invention in the non-working state;

[0042] Figure 17 Longitudinal sectional view of the fan, cleaning medium supply member and driving device of the range hood in Embodiment 4 of the present invention in the working state;

[0043] Figure 18 Schematic structural view of the range hood according to a preferred embodiment of the present invention;

[0044] Figure 19 Shows Figure 18 A-A sectional view schematic of the range hood in;

[0045] Figure 20 Schematic diagram of the cleaning process of the self-cleaning fan in the range hood according to the above preferred embodiment of the present invention;

[0046] Figure 21 Schematic diagram of the cleaning principle of the self-cleaning fan according to the above preferred embodiment of the present invention;

[0047] Figure 22 Shows the first example of cleaning the self-cleaning fan according to the above preferred embodiment of the present invention;

[0048] Figure 23 Shows the second example of cleaning the self-cleaning fan according to the above preferred embodiment of the present invention.

[0049] Description of main component symbols: 1. Housing; 2. Fan; 21. Volute; 210. Volute tongue; 211. Relief hole; 212. Drain hole; 22. Impeller; 221. Blades; 222. Middle plate; 23. Driving member; 3. Cleaning medium supply member; 30. Penetrating part; 301. Inlet; 302. Outlet; 31. Rotating seat; 311. Rotating shaft; 312. Connecting arm; 3'. Cleaning medium supply member; 30'. Penetrating part; 31'. First transmission member; 311'. First rack; 312'. First gear; 313'. Elastic limit block; 302'. Outlet; 3". Cleaning medium supply member; 30". Penetrating part; 31". Second transmission member; 311". Second rack; 312". Second gear; 302". Outlet; 313". Limit sleeve; 3131". Bending channel; 4. Driving device; 5. Water tank; 6. Steam generator; 7. Water receiving box; 8. Sensor; 1A. Range hood; 10A. Housing; 20A. Self-cleaning fan; 21A. Fan main body; 211A. Volute; 2110A. Relief hole; 212A. Impeller; 210A. Central axis; 2120A. Blades; 22A. Cleaning device; 2201A. Impact area; 2202A. Sputtering area; 221A. Cleaning medium supply member; 2210A. Spray hole; 2211A. Moving part; 22111A. First end; 22112A. Second end; 2212A. Nozzle; 222A. Driving mechanism; 223A. Rotating seat; 2231A. Rotating shaft; 2232A. Connecting arm.

[0050] The above description of main component symbols further elaborates on the present invention in conjunction with the accompanying drawings and specific embodiments. Specific embodiments

[0051] Next, the technical solutions in the embodiments of the present invention will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present invention.

[0052] It should be noted that when a component is referred to as being "installed on" another component, it can be directly on the other component or there may also be an intermediate component. When a component is considered to be "set on" another component, it can be directly set on the other component or there may be an intermediate component at the same time. When a component is considered to be "fixed to" another component, it can be directly fixed to the other component or there may be an intermediate component at the same time.

[0053] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as those commonly understood by those skilled in the art to which the present invention belongs. The terms used herein in the specification of the present invention are only for the purpose of describing specific embodiments and are not intended to limit the present invention. The term "or / and" used herein includes any and all combinations of one or more of the related listed items.

[0054] Embodiment 1:

[0055] like Figures 1 to 12 The first preferred embodiment of the range hood of the present invention is shown in FIG.

[0056] The fan 2 is disposed in the housing 1, and includes a volute 21, an impeller 22 disposed in the volute 21, and a driving member 23 for driving the impeller 22 to rotate. Figure 3 As shown, a clearance hole 211 is opened on the annular wall of the volute 21 at the position of the volute tongue 210, and a drainage hole 212 is opened at the bottom of the volute 21; and a plurality of blades 221 extending in the axial direction are arranged at intervals along the circumferential direction on the impeller 22.

[0057] The cleaning medium supply member 3 is tubular, and has a front section, a middle section, and a rear section in sequence along the flow direction of the cleaning medium. The end surface of the front section of the cleaning medium supply member 3 has an inlet 301 for the cleaning medium to enter, and the middle and rear sections of the cleaning medium supply member 3 are recorded as a penetration portion 30. The penetration portion 30 is a rigid member that can extend into the volute 21. The end surface of the penetration portion 30 has an outlet 302 for the cleaning medium to eject. In this embodiment, the cleaning medium supply member 3 is a rigid member as a whole.

[0058] The driving device 4 is a motor, which is installed at the volute tongue 210 of the volute 21, and its power output shaft is connected to the cleaning medium supply member 3 through the rotating seat 31. Specifically, the rotating seat 31 includes a rotating shaft 311 and a connecting arm 312, and the rotating shaft 311 is coaxially connected to the power output shaft of the driving device 4; the first end of the connecting arm 312 is connected to the outer peripheral wall of the rotating shaft 311, and the second end is connected to the front section of the cleaning medium supply member 3.

[0059] The driving device 4 is started to drive the penetration portion 30 of the cleaning medium supply member 3 to pass through the clearance hole 211 and rotate relative to the axis of the rotating shaft 311 to perform a swinging motion (i.e., a reciprocating motion around a certain axis within a certain angle range), so that the cleaning medium supply member 3 has at least two states:

[0060] In the working state, the outlet 302 of the threading part 30 extends into the volute 21 and faces the blade 221 of the impeller 22, and the spraying area where the cleaning medium ejected from the outlet 302 of the threading part 30 hits the blade 221 reciprocates between the two axial ends of the impeller 22, so as to clean the impeller 22, and the cleaning range of the cleaning medium covers the entire impeller 22;

[0061] In the non-working state, the outlet 302 of the threading part 30 withdraws from the volute 21 to prevent the outlet 302 of the threading part 30 from being blocked.

[0062] In the present invention, the "spraying area" refers to the range formed once the cleaning medium ejected from the outlet 302 comes into contact with the blade 221 of the impeller 22, and does not include the area formed after the cleaning medium flows along the blade 221 or drips from the blade 221 after hitting the blade 221. The shape and size of the spraying area are related to the structure and shape of the outlet 302 itself and the movement mode of the threading part 30. The present invention does not limit the shape and size of the spraying area, as long as the spraying area can clean the part between the two axial ends of the impeller 22 through reciprocating movement when the cleaning device is working.

[0063] In addition, as Figure 3 shown, since the movement trajectory of at least one end of the threading part 30 away from the outlet 302, i.e., point B, is non-linear, when the outlet 302 of the threading part 30 moves to the position of the relief hole 211, the minimum distance L between the end of the threading part 30 away from the outlet 302, i.e., point B, and the volute 21 is less than the length of the threading part 30. In this way, the cleaning medium supply member 3 can cover a larger cleaning range within a smaller movement space. On the one hand, it occupies less space, and on the other hand, the modification of the original structure of the fan is small (i.e., only a relief hole 211 for the threading part 30 to pass through needs to be opened on the volute 21), without affecting the performance of the fan.

[0064] In order to ensure that the injection area where the cleaning medium ejected from the outlet 302 of the penetration part 30 hits the blade 221 reciprocates between the two axial ends of the impeller 22, the rotation axis of the penetration part 30 is arranged at an angle with the central axis of the impeller 22 (that is, the included angle between the rotation axis of the penetration part 30 and the central axis of the impeller 22 is greater than 0° and less than 180°, which means that the rotation axis of the penetration part 30 is neither parallel nor overlapping with the central axis of the impeller 22). The reason is that when the rotation axis of the penetration part 30 is parallel or overlapping with the central axis of the impeller 22, the injection area where the cleaning medium ejected from the outlet 302 of the penetration part 30 hits the blade 221 will reciprocate along the circumferential direction of the impeller 22. In this way, when the rotating penetration part 30 sprays steam on the rotating impeller 22, the above-mentioned injection area can only cover a very narrow annular surface on the outer circumference of the impeller 22 and cannot cover other positions of the impeller 22 in the axial direction. The rotation of the penetration part 30 loses its meaning because in this case, the same cleaning effect can be achieved even if the penetration part 30 does not rotate. In this embodiment, the rotation axis of the penetration part 30 is perpendicular to the central axis of the impeller 22, and the plane where the rotation trajectory of any point at the outlet 302 of the penetration part 30 is located is arranged parallel to the central axis of the impeller 22. In this way, the injection area where the cleaning medium ejected from the outlet 302 of the penetration part 30 hits the blade 221 will move along the axial direction of the impeller 22, that is, the length direction of the blade 221, and the stroke is the shortest. Of course, in actual application, it may not be possible to accurately ensure that the movement trajectory of the above-mentioned injection area is completely parallel to the central axis of the impeller 22. When the movement trajectory deviates from the central axis of the impeller 22 by a certain angle, the entire impeller 22 can still be cleaned, but the stroke of the injection area will be relatively extended.

[0065] In order to avoid interference between the penetration part 30 and the volute 21 during the rotation process when the aperture of the relief hole 211 is small, the part of the penetration part 30 passing through the relief hole 211 during movement is an arc segment, and the center of the arc segment is located on the axis of the rotating shaft 311 (that is, the rotation axis of the penetration part 30). Denote the outer diameter of the arc segment as D1 and the aperture of the relief hole 211 as D2. The relationship between D1 and D2 satisfies: D1 ≤ D2 ≤ 1.2D1. Of course, it is best to design D1 = D2, so that it can be ensured that during the rotation process, the arc segment of the penetration part 30 always blocks the relief hole 211. On the one hand, it can prevent the cleaning medium and oil stain in the volute 21 from splashing out through the relief hole 211, and on the other hand, it can avoid affecting the normal operation of the fan 2. Of course, in actual application, the shape of the relief hole 211 can also be designed into a square or other shapes, as long as the cross-sectional shape of the arc segment is adapted to the shape of the relief hole 211.

[0066] In addition, through experimental verification, as Figure 7As shown, for the double-inlet impeller (the impeller 22 has a middle disk 222), generally, the front end is the main air inlet, and the rear end is the secondary air inlet. The oil stains are concentrated at the position where the blades 221 pass through the middle disk 222. Based on the above phenomenon, in this embodiment, when arranging the cleaning medium supply member 3, it will be arranged close to the middle disk 222 so that when the spraying area corresponds to the middle disk 222 (that is, the spraying area moves to the position where the blades 221 pass through the middle disk 222), the spraying path from the outlet 302 of the penetrating part 30 to the impeller 22 is the shortest. Under the same spraying conditions, the shorter the spraying path, the greater the spraying force, which helps to uniformly clean the entire impeller according to the distribution amount of the oil stains.

[0067] To ensure that the flushing time for each point on the blade 221 is basically the same, it is necessary to set the reciprocating motion of a point A in the axial direction between the two ends of the impeller 22 in the axial direction of the spraying area where the cleaning medium is sprayed onto the impeller 22 as a uniform motion, and the motion of the penetrating part 30 should be set as a variable motion. The derivation formula is as follows:

[0068] As Figure 8 shown, θ is the angular position corresponding to the penetrating part 30 at different times. Taking Δt as the unit time, the variable motion is decomposed into several uniform motions. Select any one of the uniform motions. Then, when Δt approaches 0, the rotation angle Δθ of the penetrating part 30 within this unit time is:

[0069]

[0070] Since v0t = h tanθt, that is

[0071] Therefore,

[0072] Among them, the point A in the spraying area where the cleaning medium is sprayed onto the impeller 22 is defined as being ejected from the point A0 at the outlet 302 of the penetrating part 30; ω is the rotational speed of the penetrating part 30; θ is the rotation angle of the penetrating part 30; h is the minimum distance from the rotation center of the point A0 at the outlet 302 of the penetrating part 30 to the blade 221 where the point A in the spraying area is sprayed; v0 is the moving speed of the point A in the spraying area.

[0073] In this embodiment, when t = 0, θ = 0.

[0074] The water tank 5 has a water inlet end and a water outlet end and is used to store water. In this embodiment, the top of the water tank 5 has an opening as the water inlet end.

[0075] The steam generator 6 has a water inlet end and a steam outlet end, and is capable of heating water to generate steam. The water inlet end of the steam generator 6 is connected to the water outlet end of the water tank 5 through a water pipe 61, and the steam outlet end of the steam generator 6 is connected to the inlet 301 of the cleaning medium supply member 3 through a steam pipe 62. In this embodiment, a water suction pump is integrated at the water inlet end of the steam generator 6.

[0076] The top of the water receiving box 7 has an opening. The water receiving box 7 is located directly below the drain hole 212 of the volute 21 and is used to receive the sewage discharged from the drain hole 212. In this embodiment, the right side wall of the water tank 5 and the left side wall of the water receiving box 7 share a side wall, which is convenient for installation.

[0077] Since self-cleaning requires the user to add clean water and pour out waste water, the amount of water is a factor that the user cares about. If too much water is required during the cleaning process, it will make women with less strength feel strenuous to operate, affecting the user experience and reducing the product satisfaction. Similarly, if the user needs to wait beside the range hood and add clean water and pour out waste water multiple times, it will dissatisfy office workers with a fast work rhythm. Therefore, the water consumption of the range hood self-cleaning technology should be small, and thus the capacities of the water tank 5 and the water receiving box 7 are approximately 650 ml.

[0078] The sensor 8 is installed at a position near the outlet 302 of the penetrating portion 30 and is used to detect the amount of oil stains at each position along the axial direction between the two end portions of the impeller 22 in the axial direction. In this embodiment, the sensor 8 is a humidity sensor. After the impeller 22 is cleaned, there will be local remaining oil stains. After the impeller 22 is centrifugally thrown away at high speed, the water and flowing oil stains on the blade 221 are thrown away, and its metal surface is in a dry state. While the surface humidity of the oil stain is much higher than that of the metal blade surface after adsorbing water. At this time, the humidity sensor can detect the oil stain with high water content to locate the oil stain. Specifically, during the rotation of the penetrating portion 30, the sensor 8 will rotate synchronously, and the detection area where the detection medium emitted from the sensor 8 shoots towards the blade 221 will reciprocate along the axial direction of the impeller 22, that is, the length direction of the blade 221, so as to detect the humidity of the corresponding detection area. After the impeller 22 is centrifugally thrown away at high speed, the water at the position with less oil stain is easily thrown away, and the water residue at the position with more oil stain will be relatively more. Therefore, the higher the humidity, the more the amount of oil stain; by extension, a surface temperature detection sensor can also be used. Due to the different thermal conductivity coefficients of the metal and the oil stain, within a short time of centrifugal throwing, there will be an obvious temperature difference between the metal surface and the oil stain surface, and the oil stain can be identified by using the thermal imaging principle to achieve the purpose of detecting the oil stain.

[0079] Of course, the above-mentioned cleaning medium supply member 3, drive device 4, water tank 5, steam generator 6, water receiving box 7 and sensor 8 can also form an independent cleaning device. This cleaning device is not limited to cleaning the impeller 22, and can also be used to clean other components in the range hood that are stained with oil, such as the inner wall of the volute 21. In this cleaning device, the passing part 30 of the cleaning medium supply member 3 serves as a moving part and makes a swinging motion under the drive of the drive device 4, so that the outlet 302 of the moving part has an arc-shaped motion trajectory. In this way, under the condition that the activity range of the cleaning medium supply member 3 is small, the cleaning medium ejected from the outlet 302 of the moving part can cover a larger cleaning range. This cleaning device occupies a small space and has a wide cleaning range. In addition, since the moving part is arc-shaped and the center of the moving part is located on the rotation axis of the moving part, the activity range of the moving part can be minimized as much as possible to avoid occupying too much space.

[0080] The working principle of this embodiment is as follows:

[0081] (1) Start the driving member 23, drive device 4 and steam generator 6. The water in the water tank 5 enters the steam generator 6 through the water pipe 61. The steam generator 6 heats the water to generate steam and transports the steam to the cleaning medium supply member 3 through the steam pipe 62. The rotating passing part 30 sprays steam at the rotating impeller 22, so that the spraying area of the steam reciprocates axially between the front end and the rear end of the impeller 22 to perform global cleaning on the entire impeller 22:

[0082] ① As Figure 4 shown, the cleaning medium supply member 3 is in the initial position, and the steam ejected from the outlet 302 of the passing part 30 aims at the rear edge of the blade 221 and sprays;

[0083] ② As Figure 5 shown, as the cleaning medium supply member 3 rotates further, the position aimed at by the outlet 302 of the passing part 30 moves forward, and the spraying area of the steam slowly moves forward;

[0084] ③ As Figure 6 shown, when the spraying area reaches the frontmost end of the blade 221, the drive device 4 changes the rotation direction and starts secondary flushing of the blade 221;

[0085] ④ Until the spraying area returns to the rearmost end of the blade 221, the drive device 4 changes the rotation direction again and repeats the above movement;

[0086] When cleaning is completed, in the non-working state, the cleaning medium supply member 3 rotates outward and completely disengages from the clearance hole 211, so that the outlet 302 of the penetration portion 30 exits the volute 21, and the risk of clogging the outlet 302 of the penetration portion 30 due to long-term placement in the volute 21 is avoided as much as possible. However, since the clearance hole 211 is no longer blocked, the airflow in the volute 21 is still easy to rush to the outlet 302 of the penetration portion 30 through the clearance hole 21, causing it to be blocked;

[0087] (2) After the overall cleaning is completed, the impeller 22 starts to rotate at a high speed to throw the grease and cleaning liquid away from the impeller 22, and then the grease test sensor is started to detect the grease on the blade 221, and the test result is recorded in the database;

[0088] After the overall cleaning, high-speed centrifugal force is used to throw away the loosened oil and cleaning water, reducing the burden of precise cleaning. The liquid oil-water mixture covering the surface of the oil will weaken the cleaning power of the high-pressure jet.

[0089] (3) Starting regional cleaning. During regional cleaning, the cleaning medium supply member 3 actively locates the point with oil stains and starts fixed-point cleaning until it is completely cleaned. For multiple oil stains, the areas are sorted and the area with the largest oil stain area is cleaned first;

[0090] Since the current self-cleaning technology requires users to add water by themselves, if too much water is added each time, it will become a burden and risk for users to add water, store waste water, and dump waste water. In addition, under normal circumstances, the impeller 22 cannot be cleaned completely through a complete cleaning. Regional cleaning can give priority to cleaning the locations with more oil spots, thereby effectively improving the cleaning rate.

[0091] like Figure 9 As shown, the range hood provides a self-cleaning reminder by the following method before self-cleaning:

[0092] S001, start, read the time T1 from the last cleaning to the present, read the cumulative use time T2 from the last cleaning to the present, and enter S002;

[0093] S002, determine whether the values of T1 and T2 satisfy: T1>D and T2>H, if so, proceed to S003, if not, proceed to S005;

[0094] S003, light up the self-cleaning prompt and enter S004;

[0095] S004, determine whether the user starts self-cleaning, if yes, go to S005, if not, return to S003;

[0096] S005, turn off the self-cleaning prompt, end;

[0097] Among them, D is the maximum allowable cleaning interval time under normal conditions. Grease is easy to be removed when it just adheres to the surface of the impeller. As time goes by, the adhered grease will gradually oxidize, and it is efficient to clean the grease before it oxidizes. Therefore, the value of D is preferably 1 to 180 days, and the best is 90 days, at this time the grease oxidation rate is low;

[0098] H is the maximum allowable cumulative usage time under normal conditions. For some users who use less usually, this scheme defines the cumulative time length from the last cleaning to the present. For users who use less usually, there is no need to clean frequently. The value of H is preferably 1 to 180 h, and the best is 60 h.

[0099] The control method for the self-cleaning operation of the above-mentioned range hood includes the following steps:

[0100] Step 1: Spray the cleaning medium through the moving cleaning medium supply member 3 onto the rotating impeller 22, so that the spraying area of the cleaning medium reciprocates axially between the front end and the rear end of the impeller 22 to perform global cleaning on the entire impeller 22;

[0101] Specifically, as Figure 10 shown, the above Step 1 is realized by the following method:

[0102] S101: Start. The initial value of θ is 0, the initial value of t is 0, start the driving member 23 to drive the impeller 22 to rotate, and enter S102;

[0103] S102: Start the driving device 4 to drive the cleaning medium supply member 3 to rotate forward, ω = f(θ), record ta, and enter S103;

[0104] S103: Collect the values of t and θ, and enter S104;

[0105] S104: Judge whether the θ value satisfies: θ≥θmax. If so, enter S106; if not, enter S105;

[0106] S105: Judge whether the t value satisfies: t - ta≥Δt. If so, return to S102; if not, return to S103;

[0107] S106: Start the driving device 4 to drive the cleaning medium supply member 3 to rotate backward, ω = f(t), record tb, and enter S107;

[0108] S107: Collect the values of t and θ, and enter S108;

[0109] S108: Judge whether the θ value satisfies: θ≤0. If so, enter S110; if not, enter S109;

[0110] S109. Determine whether the t value satisfies: t - tb ≥ Δt. If so, return to S106; if not, return to S107;

[0111] S110. Determine whether the t value satisfies: t ≥ t0. If so, proceed to S111; if not, return to S102;

[0112] S111. Turn off the driving part 23 and the driving device 4 to end;

[0113] Wherein, θmax is the rotation angle when the spraying area of the cleaning medium supply part 3 is located at the forefront of the impeller 22, and its value is preferably 30 - 75°;

[0114] Δt is the time interval between two adjacent speed changes of the driving device 4. The smaller this value is, the more it can ensure that the reciprocating movement along the axial direction between one point A of the spraying area where the cleaning medium shoots towards the impeller 22 and the two axial ends of the impeller 22 is a uniform motion. This value is preferably 1 - 100 ms;

[0115] t0 is the total global cleaning duration, and its value is preferably 10 - 20 min;

[0116] Of course, it is also possible to use Δθ as the rotation angle interval between two adjacent speed changes of the driving device 4, and this value is preferably 0.1 - 1°.

[0117] In addition, a stepping motor can also be used as the driving device 4. In this way, as Figure 11 shown, the above step one can be realized by the following method:

[0118] S101. Start. The initial value of θ is 0, the initial value of n is 0. Start the driving part 23 to drive the impeller 22 to rotate, and proceed to S102;

[0119] S102. Start the driving device 4 to drive the cleaning medium supply part 3 to rotate forward, ω = f(θ), record na, and proceed to S103;

[0120] S103. Collect the n and θ values, and proceed to S104;

[0121] S104. Determine whether the θ value satisfies: θ ≥ θmax. If so, proceed to S106; if not, proceed to S105;

[0122] S105. Determine whether the n value satisfies: n - na ≥ Δn. If so, return to S102; if not, return to S103;

[0123] S106. Start the driving device 4 to drive the cleaning medium supply part 3 to rotate backward, ω = f(t), record nb, and proceed to S107;

[0124] S107. Collect the n and θ values, and proceed to S108;

[0125] S108. Determine whether the θ value satisfies: θ ≤ 0. If so, proceed to S110; if not, proceed to S109;

[0126] S109. Determine whether the n value satisfies: n - nb ≥ Δn. If so, return to S106; if not, return to S107;

[0127] S110. Determine whether the t value satisfies: t ≥ t0. If so, proceed to S111; if not, return to S102;

[0128] S111. Turn off the driving member 23 and the driving device 4 to end;

[0129] Wherein, n is the number of steps of the stepping motor. Since the stepping motor step angle = 360° / (number of rotor teeth * n), the value of θ can be calculated when n is determined;

[0130] Δn is the step interval between two adjacent speed changes of the stepping motor, and this value is preferably 1 - 200.

[0131] Step two: Generate centrifugal force by rotating the impeller 22 to remove the cleaning medium and grease on the surface of the impeller 22;

[0132] Specifically, the above step two is realized by the following method: Start the driving member 23, set the rotation speed at 1500 - 3000 r / min, perform dehydration and deoiling for 0.1 - 10 min, and then turn off the driving member 23;

[0133] Step three: Detect the amount of oil stains at each position along the axial direction between the two end parts of the impeller 22 in the axial direction by rotating the sensor 8, and collect the oil-stained area of the impeller 22;

[0134] Specifically, as Figure 12 shown, the above step three is realized by the following method:

[0135] S301. Start. The initial value of θ is 0, the initial value of t is 0, the initial value of tc is 0, the initial value of n is 1. Start the sensor 8 and proceed to S302;

[0136] S302. Start the driving device 4 to drive the cleaning medium supply member 3 to rotate forward, ω = f(θ), record ta, and proceed to S303;

[0137] S303. Determine whether the t value satisfies: t - tc ≥ Δt'. If so, proceed to S304; if not, proceed to S307;

[0138] S304. Collect Record tc and proceed to S305;

[0139] S305. Determine whether the value satisfies: If so, proceed to S306; if not, proceed to S307;

[0140] S306. Record θn, set n = n + 1, and proceed to S307;

[0141] S307. Collect the values of t and θ, and proceed to S308;

[0142] S308. Determine whether the value of θ satisfies: θ ≥ θmax. If so, proceed to S3010; if not, proceed to S309;

[0143] S309. Determine whether the value of t satisfies: t - ta ≥ Δt. If so, return to S302; if not, return to S303;

[0144] S3010. Turn off the drive device 4 and the sensor 8, and end;

[0145] Where θmax is the rotation angle when the injection area of the cleaning medium supply member 3 is at the foremost end of the impeller 22, and its value is preferably 30 - 75°;

[0146] Δt is the time interval between two adjacent speed changes of the drive device 4. The smaller this value, the more it can ensure that the reciprocating movement of the injection area of the cleaning medium hitting one of the points A on the impeller 22 along the axis between the two axial ends of the impeller 22 is a uniform motion. This value is preferably 1 - 100 ms;

[0147] Δt’ is the time interval between two adjacent samplings of the sensor 8. The smaller this value, the greater the sampling accuracy. This value is preferably 1 - 100 ms;

[0148] is the maximum oil stain characterization value allowed in the normal state. In this embodiment, its value is preferably 20 - 100% (humidity);

[0149] Step Four: Inject the cleaning medium onto the rotating impeller 22 by moving the cleaning medium supply member 3, so that the injection area of the cleaning medium reciprocates axially between the front end and the rear end of the oil-stained area, and perform area cleaning on the oil-stained area.

[0150] Specifically, the above step 4 is implemented by the following method: first, the oily areas collected in step 3 are sorted by area size, and then the oily areas are cleaned in descending order of area size, that is, the cleaning medium supply member 3 is rotated to the corresponding rotation angle θ'n for regional cleaning. Since there is a stable angle between the sensor 8 and the cleaning medium supply member 3, it is necessary to use Δθ' to correct the step difference during data processing, that is, θ'n=θn+Δθ', Δθ' is the angle between the cleaning medium injection path of the cleaning medium supply member 3 and the medium ejection path detected by the sensor 8; as for how to sort the oily areas by area size, in this embodiment, the above-mentioned recorded θ1, θ2, ..., θn are analyzed to determine whether two consecutive oily points, three oily points, ... are found. Specifically, it is achieved by detecting whether the angles of two adjacent oily points are the rotation angles within one unit time, and whether the three consecutive oily points are the rotation angles within two unit times, and finally accurate cleaning is achieved in reverse order, because the later it is recorded in the database, the more consecutive it is.

[0151] Embodiment 2:

[0152] like Figure 13 FIG. 2 is a second preferred embodiment of the range hood of the present invention. The difference from the first embodiment is that:

[0153] In this embodiment, Figure 13 As shown, in the non-working state, the end face of the penetration portion 30 is opposite to the clearance hole 211, and the outlet 302 of the penetration portion 30 is located on the adjacent side wall of the end face. In this way, in the non-working state, the airflow in the volute 21 is no longer easy to rush to the outlet 302 of the penetration portion 30 through the clearance hole 21 to cause blockage.

[0154] Embodiment 3:

[0155] like Figure 14 and Figure 15 The third preferred embodiment of the range hood of the present invention is shown in FIG. The difference from the second embodiment is that:

[0156] In this embodiment, the cleaning medium supply member 3' is in a spiral shape, and the rear section is the penetrating portion 30'. The cleaning medium supply member 3' is drivingly connected to the power output end of the driving device 4 through the first transmission assembly 31'. The first transmission assembly 31' includes a first rack 311', a first gear 312' and an elastic limiting block 313'. Specifically, the first rack 311' is arranged on the first side of the cleaning medium supply member 3' along the extending direction of the cleaning medium supply member 3'; the first gear 312' is coaxially connected to the power output end of the driving device 4 and meshes with the first rack 311'; the elastic limiting block 313' is installed on the volute 21 and is located on the second side of the cleaning medium supply member 3', so that the cleaning medium supply member 3' is clamped between the first gear 312' and the elastic limiting block 313'.

[0157] Start the driving device 4 to drive the first gear 312' to rotate. Since the first rack 311' meshes with the first gear 312', the first rack 311' drives the cleaning medium supply member 3' to make a spiral curve movement relative to the volute 21.

[0158] The working principle of this embodiment is as follows:

[0159] (1) As Figure 14 shown, in the non-working state, the outlet 302' of the penetrating portion 30' exits the volute 21 to avoid the risk of blockage of the outlet 302' of the penetrating portion 30" caused by being placed in the volute 21 for a long time;

[0160] (2) When cleaning is required, the driving device 4 drives the cleaning medium supply member 3' to make a spiral curve movement relative to the volute 21, so that the outlet 302' of the penetrating portion 30' extends into the volute 21 and faces the blade 221 of the impeller 22. As Figure 15 shown, in the working state, by periodically changing the rotation direction of the driving device 4, the injection area where the cleaning medium ejected from the outlet 302' of the penetrating portion 30' shoots at the blade 221 can reciprocate between the two axial ends of the impeller 22, realizing the cleaning of the impeller 22.

[0161] Embodiment 4:

[0162] As Figure 16 and Figure 17 shown, this is the fourth preferred embodiment of the range hood of the present invention. The difference from Embodiment 2 is:

[0163] In this embodiment, the relief hole 211 is formed in the end wall of the volute 21. The cleaning medium supply member 3" is an elastic strip-shaped pipeline, and the rear section thereof is a penetrating portion 30". The cleaning medium supply member 3" is drivingly connected to the power output end of the driving device 4 through a second transmission assembly 31". The second transmission assembly 31" includes a second rack 311", a second gear 312" and a limiting sleeve 313". Specifically, the number of the second racks 311" is at least two, which are sequentially sleeved on the cleaning medium supply member 3" along the extending direction of the cleaning medium supply member 3", and the adjacent ends of the adjacent two second racks 311" are hinged; the second gear 312" is coaxially connected to the power output end of the driving device 4 and can be engaged with each second rack 311"; the limiting sleeve 313" is installed on the volute 21, and has a bent channel 3131" for the cleaning medium supply member 3" and the second rack 311" to pass through.

[0164] Start the driving device 4 to drive the second gear 312" to rotate. Since the second rack 311" can be engaged with each second gear 312", the second rack 311" drives the cleaning medium supply member 3' to move relative to the volute 21. During the movement, the outlet 302" of the penetrating portion 30" moves in a straight line, and the end of the penetrating portion 30" away from the outlet 302" moves along the bent channel 3131". Its movement trajectory is a non-straight shape, and the non-straight line can be a curve, a broken line, etc., which can be a regular trajectory or an irregular trajectory, as long as it is ensured that it is not a straight-line movement.

[0165] The working principle of this embodiment is as follows:

[0166] (1) As Figure 16 shown, in the non-working state, the outlet 302" of the penetrating portion 30" exits the volute 21 to avoid the risk of blockage of the outlet 302" of the penetrating portion 30" caused by being placed in the volute 21 for a long time. Moreover, the cleaning medium supply member 3" is arranged along the bent channel 3131" under the limitation of the limiting sleeve 313", reducing the occupied space;

[0167] (2) When cleaning is required, the driving device 4 drives the cleaning medium supply member 3" to move backward relative to the volute 21 so that the outlet 302" of the penetrating portion 30" extends into the volute 21 and faces the blade 221 of the impeller 22. As Figure 17 shown, in the working state, the cleaning medium supply member 3" extending into the volute 21 will recover to a long strip structure under its own elastic force. By periodically changing the rotation direction of the driving device 4, the spraying area where the cleaning medium ejected from the outlet 302" of the penetrating portion 30" shoots at the blade 221 can reciprocate between the two axial ends of the impeller 22, realizing the cleaning of the impeller 22; the cleaning medium supply member 3" exposed outside the volute 21 is arranged along the bent channel 3131" under the limitation of the limiting sleeve 313", reducing the occupied space.

[0168] It should be noted that in the above-mentioned Embodiments 1 to 3 of the present application, the cleaning medium supply member 3 (3') is rotatable relative to the volute 21 of the blower 2, so that the cleaning area where the cleaning medium ejected from the cleaning medium supply member 3 (3') shoots towards the impeller 22 reciprocates between the two axial ends of the impeller 22, so as to realize the cleaning of the entire impeller. However, the impeller 22 of the blower 2 usually rotates at a constant speed. If the cleaning medium supply member 3 (3') also rotates at a constant speed relative to the volute 21, the central axial distance between adjacent cleaning areas on each blade 221 is constantly changing, and the closer to the axial ends of the impeller 22, the larger this central axial distance becomes, resulting in a gap between two adjacent cleaning areas, and the full-area cleaning of the impeller 22 cannot be truly achieved. If the rotation of the cleaning medium supply member 3 (3') and / or the impeller 22 is reduced so that there is no gap between adjacent cleaning areas near the axial ends of the impeller 22 on the blade 221, not only will the cleaning time be greatly increased, but also the adjacent cleaning areas far from the axial ends of the impeller 22 on the blade 221 will seriously overlap, consuming a large amount of cleaning medium and causing waste of water resources.

[0169] Therefore, in order to save water resources while achieving true full-area cleaning, the design of the rotational speed relationship between the cleaning medium supply member 3 (3') and the impeller 22 in the present application is particularly important. That is to say, how to reasonably design the rotational speed relationship between the cleaning medium supply member 3 (3') and the impeller 22 is the key to truly achieving full-area cleaning to obtain a better cleaning effect.

[0170] Specifically, according to another aspect of the present application, as Figures 18 to 23 shown, a preferred embodiment of the present application provides a range hood 1A, which may include a housing 10A and a self-cleaning blower 20A assembled in the housing 10A for sucking oil fumes. It can be understood that the range hood 1A of the present application may also but is not limited to include a water tank, a steam generator, a water receiving box and / or a sensor to assist in completing the oil fume suction function, which will not be elaborated herein.

[0171] More specifically, as Figures 19 to 23As shown, the self-cleaning fan 20A of the present application may include a fan main body 21A and a cleaning device 22A. The fan main body 21A may include a volute 211A and an impeller 212A rotatably disposed within the volute 211A. A plurality of blades 2120A are circumferentially provided on the impeller 212A. The cleaning device 22A may include a cleaning medium supply member 221A rotatably disposed relative to the volute 211A. When the self-cleaning fan 20A performs self-cleaning, the impeller 212A and / or the cleaning medium supply member 221A rotate at a variable speed relative to the volute 211A, and the cleaning medium supply member 221A is configured to spray a cleaning medium onto the blades 2120A to form a plurality of impact regions 2201A arranged axially on the surface of each blade 2120A and a plurality of sputtering regions 2202A corresponding to and surrounding the impact regions 2201A one by one; wherein the center distance S0 between two axially adjacent impact regions 2201A on each blade 2120A is greater than or equal to the axial dimension S1 of the impact region 2201A and less than or equal to the axial dimension S2 of the sputtering region 2202A; that is, S1 ≤ S0 ≤ S2. It can be understood that the fan main body 21A mentioned in the present application further includes a driving member, such as a motor, for driving the impeller 212A to rotate around the central axis 210A; the axial direction mentioned in the present application refers to the extending direction of the central axis 210A of the impeller 212A.

[0172] It should be noted that the cleaning medium supply member 221A has a spray hole 2210A for spraying the cleaning medium; since the cleaning medium sprayed through the spray hole 2210A of the cleaning medium supply member 221A usually forms a spray jet, which splashes or scatters outward instantaneously when it impacts the surface of the blade 2120A, making the rinsing area larger, the cleaning medium sprayed through the cleaning medium supply member 221A will form an impact region 2201A of direct impact and a sputtering region 2202A located around the impact region 2201A on the surface of the blade 2120A to be cleaned. For example, as Figure 20As shown, the impact area 2201A mentioned in this application refers to the area where the cleaning medium sprayed by the cleaning medium supply member 221A directly impacts the surface of a certain blade 2120A after the impeller 212A rotates one week; the sputtering area 2202A mentioned in this application refers to the area where the cleaning medium sprayed by the cleaning medium supply member 221A sputters outward while directly impacting the surface of the blade 2120A. It can be understood that the impact area 2201A mentioned in this application can achieve the best cleaning effect due to the direct impact of the cleaning medium; at the same time, the sputtering area 2202A mentioned in this application can also achieve a good cleaning effect due to the sputtering of the cleaning medium. Therefore, the cleaning medium sprayed by the cleaning medium supply member 221A of this application forms an impact area 2201A and a corresponding sputtering area 2202A at any cleaning moment, which will jointly form a continuous effective cleaning area. In addition, the shapes of the impact area 2201A and the sputtering area 2202A of this application shown in the appendix are only schematic, and this application does not limit them. Figure 20 The shapes shown in the appendix are only schematic, and this application does not limit them.

[0173] In addition, since the impeller 212A rotates relative to the volute 211A while the cleaning medium supply member 221A rotates relative to the volute 211A, the two axially adjacent impact areas 2201A on the blade 2120A refer to the two areas formed by the jet impinging on the surface of the blade 2120A before and after the impeller 212A rotates one week around the central axis 210A. Then, the center distance S0 between the two axially adjacent impact areas 2201A on the blade 2120A is equal to the distance that the jet moves along the axial direction of the impeller 212A when the impeller 212A rotates one week around the central axis 210A.

[0174] In this way, when S0 > S2, there is a gap between the two axially adjacent sputtering areas 2202A on each blade 2120A, that is, the cleaning area on each blade 2120A is discontinuous and cannot achieve true full-area cleaning; when S0 < S1, there is partial overlap between the two axially adjacent impact areas 2201A on each blade 2120A, resulting in the same area on the blade 2120A being repeatedly impacted, which will not only consume a large amount of cleaning medium (such as water), causing waste of resources, but also increase the cleaning time, resulting in low cleaning efficiency. However, in the self-cleaning fan 20A of this application, the center distance D between the two axially adjacent impact areas 2201A on each blade 2120A satisfies the condition: S1 ≤ S0 ≤ S2, which can not only achieve true full-area cleaning, but also avoid waste of water resources, shorten the cleaning time, and improve the cleaning efficiency.

[0175] Optionally, the rotation axis of the cleaning medium supply member 221A is eccentrically perpendicular to the central axis 210A of the impeller 212A, ensuring that the jet formed by the cleaning medium sprayed by the cleaning medium supply member 221A can move along the axial direction of the impeller 212A. It is understood that the rotation axis mentioned in the present application refers to the straight line around which the cleaning medium supply member 221A rotates relative to the volute 211A.

[0176] According to the above embodiments of the present application, Figure 19 and Figure 20 As shown, the cleaning medium supply member 221A includes a moving portion 2211A extending in the circumferential direction of the rotation axis and a nozzle 2212A extending from the first end 22111A of the moving portion 2211A. Optionally, the nozzle 2212A tilts outward from the first end 22111A of the moving portion 2211A, that is, the angle β between the jet of the nozzle 2212A and the tangent of the moving portion 2211A at the first end 22111A is greater than 0° and less than or equal to 90°. In this way, compared with the solution in which the nozzle 2212A extends in the circumferential direction or tangential direction of the moving portion 2211A, when the cleaning medium supply member 221A is rotated to clean the entire blade 2120A, the average distance between the nozzle 2212A and the blade 2120A in this embodiment of the present application is shorter, which helps to reduce the loss of flushing force. It can be understood that the spray hole 2210A of the cleaning medium supply member 221A of the present application can be provided by the nozzle 2212A.

[0177] It is worth noting that the axial dimension S1 of the impact area 2201A and the axial dimension S2 of the sputtering area 2202A mentioned in the present application are usually related to the inner diameter d of the nozzle hole of the nozzle 2212A, the rated pressure of the pump, and the distance from the nozzle 2212A to the cleaned blade 2120A. In order to simplify the design, the present application can define the axial dimension S1 of the impact area 2201A and the axial dimension S2 of the sputtering area 2202A by the inner diameter d of the nozzle hole of the nozzle 2212A.

[0178] Optionally, the axial dimension S1 of the impact region 2201A may be greater than the inner diameter d of the nozzle hole and less than or equal to 1.2 times the inner diameter d of the nozzle hole, i.e., d < S1 ≤ 1.2d; the axial dimension S2 of the sputtering region 2202A may be greater than 1.2 times the inner diameter d of the nozzle hole and less than or equal to 10 times the inner diameter d of the nozzle hole, i.e., 1.2d < S2 ≤ 10d. In other words, the lower limit of the center-to-center spacing S between two axially adjacent impact regions 2201A on the blade 2120A is greater than the inner diameter d of the nozzle hole and less than or equal to 1.2 times the inner diameter d of the nozzle hole; the upper limit of the center-to-center spacing S between two axially adjacent impact regions 2201A on the blade 2120A is greater than 1.2 times the inner diameter d of the nozzle hole and less than or equal to 10 times the inner diameter d of the nozzle hole, so that two axially adjacent sputtering regions 2202A partially overlap, facilitating the achievement of true full-domain cleaning while meeting the water-saving requirements and improving the cleaning effect.

[0179] Further, the axial dimension S1 of the impact region 2201A may be greater than the inner diameter d of the nozzle hole and less than or equal to 1.1 times the inner diameter d of the nozzle hole, i.e., d < S1 ≤ 1.1d; the axial dimension S2 of the sputtering region 2202A may be greater than 1.2 times the inner diameter d of the nozzle hole and less than or equal to 2 times the inner diameter d of the nozzle hole, i.e., 1.2d < S2 ≤ 2d. In other words, the lower limit of the center-to-center spacing S between two axially adjacent impact regions 2201A on the blade 2120A is greater than the inner diameter d of the nozzle hole and less than or equal to 1.1 times the inner diameter d of the nozzle hole; the upper limit of the center-to-center spacing S between two axially adjacent impact regions 2201A on the blade 2120A is greater than 1.2 times the inner diameter d of the nozzle hole and less than or equal to 2 times the inner diameter d of the nozzle hole, so that two axially adjacent sputtering regions 2202A overlap more, facilitating the obtaining of a better cleaning effect.

[0180] It should be noted that when measuring the center-to-center spacing S0, the present application can use a laser to replace the nozzle 2212A. The laser spot formed by the laser emitted by the laser on the blade 2120A is the center of the impact region 2201A. At this time, only by measuring the axial distance that the laser spot moves on the blade 2120A when the impeller 212A rotates one week can the center-to-center spacing S0 be obtained.

[0181] Further, the present application defines the points where the jet stream first impacts the surface of the blade 2120A at two moments before and after the impeller 212A rotates one week around the central axis 210A as the impact starting points, as Figure 20For the shown point a1 and point a2, the distance S between two axially adjacent impact starting points on the blade 2120A is equal to the distance that the jet flow moves along the axial direction of the impeller 212A when the impeller 212A rotates one week around the central axis 210A. At this time, only by measuring the distance between two laser spots that first appear on the surface of the same blade 2120A before and after the impeller 212A rotates one week, the distance S between two axially adjacent impact starting points on the blade 2120A can be obtained, so as to reduce the measurement difficulty.

[0182] Since the axial dimensions of the impact area 2201A and the sputtering area 2202A defined in the present application are both related to the inner diameter dimension of the spray hole, in an example of the present application, when the self-cleaning fan 20A performs self-cleaning, the distance S between two axially adjacent impact starting points a1 and a2 on each blade 2120A can be greater than or equal to the inner diameter dimension of the spray hole 2210A and less than or equal to 10 times the inner diameter dimension of the spray hole 2210A. In this way, there will be no excessive overlap between two axially adjacent impact areas 2201A on each blade 2120A, avoiding waste of water resources, and there will be no large gap, ensuring partial overlap between adjacent sputtering areas 2202A to achieve true full-area cleaning. It can be understood that the spray hole of the nozzle 2212A is usually a circular hole, then the inner diameter dimension of the spray hole 2210A mentioned in the present application is equal to the diameter of the spray hole of the nozzle 2212A; when the spray hole of the nozzle 2212A is implemented as a non-circular hole such as a strip hole, the inner diameter dimension of the spray hole 2210A mentioned in the present application is equal to the axial dimension of the spray hole of the nozzle 2212A.

[0183] Optionally, the distance S between two axially adjacent impact starting points a1 and a2 on each blade 2120A is less than or equal to 2 times the inner diameter dimension of the spray hole 2210A, so that the overlap range between two adjacent sputtering areas 2202A can be appropriately increased, which helps to improve the cleaning effect.

[0184] Optionally, the distance S between two axially adjacent impact starting points a1 and a2 on each blade 2120A is greater than or equal to 1.2 times the inner diameter dimension of the spray hole 2210A, avoiding overlap between two adjacent impact areas 2201A, which helps to further save water resources.

[0185] According to the above embodiments of the present application, the spacing S between two adjacent impact starting points a1 and a2 axially on each blade 2120A remains unchanged, that is, multiple impact starting points on each blade 2120A are evenly distributed along the axial direction of the impeller 212A, so that the impact points of the cleaning medium ejected via the cleaning medium supply member 221A on the surface of each blade 2120A are axially evenly distributed, which helps to improve the consistency of the cleaning effect. It can be understood that the uniform distribution mentioned in the present application is not absolute but relative, that is, there can be a certain fluctuation in this uniform distribution, as long as it is uniform within the allowable range of errors such as measurement errors or mechanical errors, and the present application will not elaborate on this.

[0186] It should be noted that, in order to achieve the uniform distribution of the impact starting points (or impact points), the present application can be achieved by making at least one of the impeller 212A and the cleaning medium supply member 221A rotate at a variable speed relative to the volute 211A.

[0187] Exemplarily, in the first example of the present application, as Figure 20 and Figure 22 shown, when the self-cleaning fan 20A performs self-cleaning, the impeller 212A rotates at a constant speed relative to the volute 211A, and the cleaning medium supply member 221A rotates at a variable speed relative to the volute 211A, so that all the impact regions 2201A on each blade 2120A are evenly distributed along the axial direction of the impeller 212A. It can be understood that when the impeller 212A rotates at a constant speed, if the uniform distribution of the impact points is to be achieved, then within the same time, the axial length that the nozzle 2212A can clean needs to remain consistent, that is, the axial speed of the jet flow moving on the surface of the blade 2120A to be cleaned needs to be the same.

[0188] Specifically, taking the angle β between the jet flow of the nozzle 2212A and the tangent line at the first end 22111A of the moving part 2211A being equal to 90° as an example: as Figure 21 and Figure 22 shown, the perpendicular jet distance between the rotation axis of the cleaning medium supply member 221A and the blade 2120A to be cleaned is h; when the nozzle 2212A rotates around this rotation axis by an angle θ (i.e., the rotation angle of the cleaning medium supply member 221A) from the position where the jet flow perpendicularly jets to the blade 2120A to be cleaned, so that the jet flow moves from point E to point F on the surface of the blade 2120A to be cleaned, the inclined jet distance between the rotation axis of the cleaning medium supply member 221A and the blade 2120A to be cleaned is r, and the axial speed of the jet flow on the surface of the blade 2120A to be cleaned is V0. At this time, as Figure 21 shown, by decomposing the axial speed V0, the radial speed V x and the tangential speed Vy It is understood that this application Figure 22 The point O shown refers to the real position of the rotation center of the cleaning medium supply member 221A; the point E refers to the vertical injection projection position of the rotation center of the cleaning medium supply member 221A on the surface of the cleaned blade 2120A; the point F refers to the oblique injection projection position (i.e., the position projected along the injection direction) of the rotation center of the cleaning medium supply member 221A on the surface of the cleaned blade 2120A; then the vertical injection distance h = OE; the oblique injection distance r = OF; the rotation angle θ = ∠FOE. The rotation center mentioned in the present application may refer to the intersection between the reverse extension line of the jet flow of the nozzle 2212A and the rotation axis of the cleaning medium supply member 221A.

[0189] More specifically, if Figure 21 As shown, due to the tangential velocity V of the jet on the surface of the cleaned blade 2120A y = rω, where r is the oblique spray distance between the rotation axis O and the cleaned blade 2120A, and ω is the angular velocity of the nozzle 2212A rotating around the rotation axis O; therefore, cosθ=h / r; cos∠V y FV0=V y / V0=(rω) / V0.

[0190] Furthermore, due to ∠V y FV0 = θ, so ω = (V0 cos θ) / r, and further ω = (V0 cos 2 θ) / h.

[0191] Furthermore, n represents the rotation speed of the impeller 212A, and the time for the impeller 212A to rotate one circle, that is, the rotation period T of the impeller 212A = 1 / n. In order to achieve uniform distribution of the impact points, the rotation period T of the impeller 212A needs to satisfy: T = S / V0, where S is the distance between two axially adjacent impact starting points a1 and a2 on each blade 2120A, that is, the axial displacement of the jet on the surface of the cleaned blade 2120A when the impeller 212A rotates one circle. At this time, T = 1 / n = S / V0, that is, V0 = nS. It can be understood that since the rotation speed n of the impeller 212A is constant, in order to achieve uniform distribution of the impact points (that is, S remains unchanged), the axial velocity V0 of the jet on the surface of the cleaned blade 2120A is also unchanged.

[0192] Thus, substituting V0=nS into the above formula ω=(V0cos 2 θ) / h, we can get: ω=(nScos 2θ) / h. In other words, in order to achieve a uniform distribution of the impact points, in this example of the present application, the angular velocity ω of the cleaning medium supply member 221A and the rotational speed n of the impeller 212A satisfy the relationship: ω = (nScos 2 θ) / h; where: S is the distance between two adjacent impact starting points a1 and a2 in the axial direction on each blade 2120A; θ is the rotation angle of the cleaning medium supply member 221A (i.e., the nozzle 2212A).

[0193] It can be easily seen from the above formula that: when the impeller 212A rotates at a constant speed (i.e., the rotational speed n of the impeller 212A remains unchanged), as the rotation angle θ (such as Figure 22 shown as θ1 < θ2 < θ3) increases, the angular velocity ω of the cleaning medium supply member 221A gradually decreases (i.e., the cleaning medium supply member 221A rotates at a decreasing speed), so that the distance that the jet flow moves axially on the blade 2120A in the same time t is equal (such as Figure 22 shown as M1 = M2 = M3), thereby achieving a uniform distribution of the impact points, facilitating the improvement of the cleaning efficiency while saving water resources.

[0194] Optionally, the angular velocity ω of the cleaning medium supply member 221A and the rotational speed n of the impeller 212A in the present application may satisfy the relationship: ω = (nPcos 2 θ) / h; where: P is the cleaning coefficient; θ is the rotation angle of the cleaning medium supply member 221A (i.e., the nozzle 2212A); h is the perpendicular jet distance between the rotation axis of the cleaning medium supply member 221A and the blade 2120A to be cleaned. It can be understood that the cleaning coefficient P mentioned in the present application is determined by the distance S between two adjacent impact starting points a1 and a2 in the axial direction on each blade 2120A.

[0195] Exemplarily, in the second example of the present application, as Figure 20 and Figure 23 shown, when the self-cleaning fan 20A performs self-cleaning, the impeller 212A rotates at a variable speed relative to the volute 211A, and the cleaning medium supply member 221A rotates at a constant speed relative to the volute 211A, and it can also make all the impact areas 2201A on each blade 2120A evenly distributed along the axial direction of the impeller 212A. It can be understood that when the cleaning medium supply member 221A rotates at a constant speed, the axial length that the nozzle 2212A can clean in the same time is variable, that is, the axial length S i where the jet flow moves on the surface of the blade 2120A to be cleaned is constantly changing; at this time, if a uniform distribution of the impact points is to be achieved, it is necessary to ensure that the axial length S i= nS, where n is the rotational speed of the impeller 212A, and S is the distance between two axially adjacent impact starting points a1 and a2 on each blade 2120A. That is to say, in order to achieve a uniform distribution of the impact points, the rotational speed of the impeller 212A is constantly changing at this time, that is, the impeller 212A needs to rotate at a variable speed.

[0196] Specifically, taking the example where the angle β between the jet flow of the nozzle 2212A and the tangent line at the first end 22111A of the moving part 2211A is equal to 90°: As Figure 21 and Figure 23 shown, the perpendicular injection distance between the rotation axis O of the cleaning medium supply member 221A and the blade 2120A to be cleaned is h; when the nozzle 2212A rotates around the rotation axis O by an angle θ (i.e., the rotation angle of the cleaning medium supply member 221A) from the vertical injection to the blade 2120A to be cleaned, so that the jet flow moves from point E to point F on the surface of the blade 2120A to be cleaned, the inclined injection distance between the rotation axis O of the cleaning medium supply member 221A and the blade 2120A to be cleaned is r, and the axial velocity of the jet flow moving on the surface of the blade 2120A to be cleaned is V0. At this time, by decomposing the axial velocity V0, the radial velocity V x and the tangential velocity V y of the jet flow on the surface of the blade 2120A to be cleaned can be obtained.

[0197] More specifically, as Figure 21 shown, since the tangential velocity V y of the jet flow on the surface of the blade 2120A to be cleaned = ωr, where r is the inclined injection distance between the rotation center of the cleaning medium supply member 221A and the blade 2120A to be cleaned, and ω is the angular velocity of the nozzle 2212A rotating around the rotation axis O; therefore, cosθ = h / r; cos∠V y FV0 = V y / V0 = (rω) / V0. Further, since ∠V y FV0 = θ, so h / r = (rω) / V0, and then V0 = (ωr 2 ) / h. It can be understood that since the angular velocity of the cleaning medium supply member 221A is constant, the axial velocity V0 of the jet flow moving on the surface of the blade 2120A to be cleaned also changes with the change of the injection distance r.

[0198] Furthermore, let n represent the rotational speed of the impeller 212A respectively. Then, the time for the impeller 212A to rotate one circle, that is, the rotation period T of the impeller 212A is T = 1 / n. In order to achieve a uniform distribution of the impact points, the rotation period T of the impeller 212A needs to satisfy: T = S / V0, where S is the distance between two adjacent impact starting points a1 and a2 axially on each blade 2120A, that is, the axial displacement of the jet flow on the surface of the blade 2120A during one rotation of the impeller 212A. At this time, T = 1 / n = S / V0, that is, V0 = nS. It can be understood that since the axial velocity V0 of the jet flow on the surface of the blade 2120A to be cleaned is variable, in order to achieve a uniform distribution of the impact points (i.e., S remains unchanged), the rotational speed n of the impeller 212A is also variable.

[0199] Thus, substituting V0 = nS into the above formula V0 = (ωr 2 ) / h gives: n = (ωr 2 ) / (hS). In other words, in order to achieve a uniform distribution of the impact points, in this example of the present application, the rotational speed n of the impeller 212A and the angular velocity ω of the cleaning medium supply member 221A satisfy the relational expression: n = (ωr 2 ) / (hS); in the formula: S is the distance between two adjacent impact starting points a1 and a2 axially on each blade 2120A; r is the inclined jet distance between the rotation axis O and the blade 2120A to be cleaned.

[0200] In other words, since r = h / cosθ, the above formula can be rewritten as: n = (ωh) / (Scos 2 θ); in the formula: S is the distance between two adjacent impact starting points a1 and a2 axially on each blade 2120A; θ is the rotation angle of the cleaning medium supply member 221A (i.e., the nozzle 2212A).

[0201] It can be easily known from the above formula that when the cleaning medium supply member 221A rotates at a constant speed (i.e., the angular velocity ω of the cleaning medium supply member 221A remains unchanged), as the jet distance r or the rotation angle θ (such as Figure 23 shown as θ1 < θ2 < θ3) increases, the rotational speed n of the impeller 212A gradually increases (i.e., the impeller 212A rotates at an increasing speed), so that the distance that the jet flow axially moves on the blade 2120A within the same time t gradually increases (such as Figure 23 shown as M1 < M2 < M3), thereby achieving a uniform distribution of the impact points, facilitating the improvement of the cleaning efficiency while saving water resources.

[0202] Optionally, the angular velocity ω of the cleaning medium supply member 221A and the rotational speed n of the impeller 212A of the present application can satisfy the relational expression: n = (ωr 2) / (hP); where: P is the cleaning coefficient; r and h are the cleaning injection distance and the vertical injection distance between the rotation axis of the cleaning medium supply member 221A and the blade 2120A to be cleaned, respectively. It can be understood that the cleaning coefficient P mentioned in the present application is determined by the distance S between two adjacent impact starting points a1 and a2 axially on each blade 2120A.

[0203] It should be noted that in other examples of the present application, the self-cleaning fan 20A of the present application can also achieve a uniform distribution of impact points by the cooperation of a cleaning medium supply member 221A that rotates at a variable speed and an impeller 212A that rotates at a variable speed, that is, both the cleaning medium supply member 221A and the impeller 212A rotate at a variable speed, and a uniform distribution of impact points can also be achieved.

[0204] Optionally, as the rotation angle θ of the cleaning medium supply member 221A increases, the cleaning medium supply member 221A rotates at a decreasing speed, and the impeller 212A rotates at an increasing speed, so that the impact points are evenly distributed. In other words, when the cleaning medium supply member 221A decreases in speed less, the impeller 212A needs to increase in speed appropriately to meet the uniform distribution of impact points. At this time, the time required to complete the cleaning of the entire impeller 212A is shorter, the water used will be reduced, and the cleaning effect will decline, which is suitable for the scenario where less oil stains are attached to the blades 2120A of the impeller 212A.

[0205] Optionally, as the rotation angle θ of the cleaning medium supply member 221A increases, both the cleaning medium supply member 221A and the impeller 212A can rotate at a decreasing speed, and the degree of speed reduction of the cleaning medium supply member 221A is greater than that of the impeller 212A, so that the impact points are evenly distributed. In other words, when the cleaning medium supply member 221A decreases in speed more, the impeller 212A needs to decrease in speed appropriately to meet the uniform distribution of impact points. At this time, the time required to complete the cleaning of the entire impeller 212A is longer, the water used will increase, and the cleaning effect will improve, which is suitable for the scenario where more oil stains are attached to the blades 2120A of the impeller 212A.

[0206] It should be noted that if, as the rotation angle θ of the cleaning medium supply member 221A increases, both the cleaning medium supply member 221A and the impeller 212A can also rotate at an increasing speed, and the degree of speed increase of the impeller 212A is greater than that of the cleaning medium supply member 221A, a uniform distribution of impact points can also be achieved, which helps to further shorten the cleaning time. However, it should be noted that once the rotation speed of the impeller 212A is too high, the cleaning medium will be difficult to impact the surface to be cleaned of the blade 2120A, resulting in a poor cleaning effect.

[0207] In addition, in order to further improve the cleaning effect, the rotation direction of the impeller 212A is opposite to the injection direction of the cleaning medium supply member 221A, so that the injection speed of the cleaning medium is superimposed on the rotation speed of the blade 2120A to be cleaned, which helps to enhance the impact effect and improve the cleaning rate after cleaning. For example, if the cleaning medium supply member 221A injects the cleaning medium to the left, when the impeller 212A rotates clockwise, the injection speed of the cleaning medium is superimposed on the rotation speed of the blade 2120A to be cleaned, which can enhance the impact force and improve the flushing effect; if the impeller 212A rotates counterclockwise, a part of the injection speed of the cleaning medium will be offset by the rotation speed of the blade 2120A to be cleaned, that is, a part of the injection speed of the cleaning medium will be used to catch up with the blade 2120A to be cleaned, resulting in a weakening of the impact force and a deterioration of the flushing effect.

[0208] It should be noted that, as Figure 19 shown, a relief hole 2110A is provided in the volute 211A of the fan main body 21A. The rotation axis O of the cleaning medium supply member 221A is located outside the volute 211A, and the moving part 2211A of the cleaning medium supply member 221A rotates around the rotation axis O to drive the nozzle 2212A to pass through the relief hole 2110A in and out of the volute 211A to form a penetrating part. In this way, when it is necessary to clean the impeller 212A, the moving part 2211A of the cleaning medium supply member 221A is rotated around the rotation axis O to drive the nozzle 2212A to extend into the volute 211A through the relief hole 2110A to inject the cleaning medium onto the blade 2120A; and after passing through the relief hole 2110A, the nozzle 2212A makes a swinging motion around the rotation axis O (that is, makes a reciprocating motion within a certain angle range around the rotation axis O), so that the injection area reciprocates between the two axial ends of the impeller 212A, thereby realizing the full-range cleaning of the impeller 212A; when it is not necessary to clean the impeller 212A, the moving part 2211A of the cleaning medium supply member 221A is rotated around the rotation axis O to drive the nozzle 2212A to withdraw from the volute 211A through the relief hole 2110A, preventing the nozzle 2212A from being blocked by the oil stain in the volute 211A.

[0209] It can be understood that it is precisely because the nozzle 2212A in the cleaning medium supply member 221A tilts outward that when the rotation axis O is arranged outside the volute 211A, the nozzle 2212A can ensure the full-range cleaning of the impeller 212A by starting to spray the cleaning medium only after being screwed into the volute 211A through the relief hole 2110A; when the nozzle extends in the circumferential direction, after the nozzle is screwed into the volute 211A, the angle between the spraying direction of the nozzle and the axis direction of the impeller is necessarily less than 90° and gradually decreases. At this time, not only is the impact force loss relatively large, but also the nozzle 2212A needs to spray the cleaning medium before being screwed into the volute 211A through the relief hole 2110A in order to achieve the full-range cleaning of the impeller 212A. However, in order to prevent oil fume from leaking out from the relief hole 2110A, a closing door is usually provided at the relief hole 2110A. Therefore, the nozzle cannot spray the cleaning medium onto the impeller 212A for cleaning before passing through the relief hole 2110A and being screwed into the volute 211A, resulting in the circumferentially extending nozzle being unable to clean a certain axial end of the impeller 212A and thus unable to achieve the full-range cleaning of the impeller 212A.

[0210] Optionally, as Figure 18 and Figure 19 shown, the cleaning device 22A further includes a driving mechanism 222A fixedly provided on the volute 211A and a rotating seat 223A drivably connected to the driving mechanism 222A. The rotating seat 223A includes a rotating shaft 2231A providing the rotation axis O and a connecting arm 2232A extending outward from the outer peripheral wall of the rotating shaft 2231A. The rotating shaft 2231 is coaxially connected to the power output end of the driving mechanism 222A, and the end of the connecting arm 2232A is fixedly connected to the moving part 2211A of the cleaning medium supply member 221A. In this way, the connecting arm 2232A can support the moving part 2211A and the nozzle 2212A to be away from the rotation axis O, so that the opening position of the relief hole 2110A can be away from the rotation axis O, which helps to ensure that the power output end of the driving mechanism 222A can be away from the relief hole 2110A, avoid the driving mechanism 222A being contaminated by the oil and grease leaking out from the relief hole 2110A, and helps to extend the service life of the driving mechanism 222A. It can be understood that in other examples of the present application, the driving mechanism 222A can also be fixedly provided on the housing 10A and still be able to drive the cleaning medium supply member 221A to perform a swinging motion outside the volute 211A; or, the cleaning medium supply member 221A of the present application can also be rotatably arranged on the housing 10A, which will not be elaborated herein.

[0211] Optionally, as Figure 19As shown, the end of the connecting arm 2232A is fixedly connected to the second end 22112A of the moving part 2211A, so as to leave a sufficient long distance between the nozzle 2212A and the connecting arm 2232A, so as to widen the swinging angle range of the nozzle 2212A when a relatively small relief hole 2110A is opened, and avoid structural interference between the connecting arm 2232A and the volute 211A.

[0212] Optionally, the moving part 2211A can be implemented as an arc-shaped rigid pipe, so as to minimize the opening size of the relief hole 2110A while stably supporting the nozzle 2212A; for example, the moving part 2211A can be, but is not limited to, a hollow pipe made of hard materials such as plastics, metals or polymer materials.

[0213] It should be noted that, in other examples of the present application, the impeller and the cleaning medium supply member can also be driven to rotate at variable speeds, and it is still possible to make the centers of the impact areas on each blade evenly distributed along the axial direction of the impeller, thereby achieving true full-range cleaning.

[0214] The technical features of the above embodiments can be combined arbitrarily. For the sake of brevity of description, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, it should be considered as the scope described in this specification.

[0215] The above embodiments only represent several implementation manners of the present invention, and their descriptions are relatively specific and detailed, but they should not be construed as limiting the scope of the invention patent. It should be pointed out that for those of ordinary skill in the art, without departing from the concept of the present invention, several deformations and improvements can still be made, and these all belong to the protection scope of the present invention. Therefore, the protection scope of the invention patent should be subject to the appended claims.

Claims

1. Self-cleaning fan, characterized in that, Comprising: A blower main body, the blower main body includes a volute and an impeller rotatably disposed within the volute, and a plurality of blades are circumferentially provided on the impeller; And A cleaning device, the cleaning device includes a cleaning medium supply member rotatably disposed relative to the volute, the cleaning medium supply member has spray holes for spraying a cleaning medium, when the self-cleaning blower performs self-cleaning, the impeller and / or the cleaning medium supply member rotate at a variable speed relative to the volute, and the cleaning medium supply member is used to spray the cleaning medium onto the blades to form a plurality of impact starting points arranged axially on the surface of each blade; Wherein the distance between two axially adjacent impact starting points on each blade is greater than or equal to the inner diameter size of the spray hole and less than or equal to 10 times the inner diameter size of the spray hole; The two axially adjacent impact starting points on the blade are the points where the spray flow formed by spraying the cleaning medium by the cleaning medium supply member first impacts on the blade surface at two moments before and after the impeller rotates one week around the central axis.

2. The self-cleaning fan according to claim 1, wherein The distance between two axially adjacent impact starting points on each blade is less than or equal to 2 times the inner diameter size of the spray hole.

3. The self-cleaning fan according to claim 1, wherein, The distance between two axially adjacent impact starting points on each blade is greater than or equal to 1.2 times the inner diameter size of the spray hole.

4. The self-cleaning fan according to any one of claims 1 to 3, characterized in that, The impact starting points on each blade are evenly distributed along the axial direction of the impeller.

5. The self-cleaning fan according to claim 4, wherein, The rotation axis of the cleaning medium supply member is skew perpendicular to the central axis of the impeller.

6. The self-cleaning fan according to claim 5, characterized in that, When the self-cleaning blower performs self-cleaning, the impeller rotates at a uniform speed relative to the volute, and the cleaning medium supply member rotates at a variable speed relative to the volute.

7. The self-cleaning fan according to claim 6, characterized in that, The angular velocity ω of the cleaning medium supply member and the rotational speed n of the impeller satisfy the relational expression: ω = (nPcos 2 θ) / h; where: P is the cleaning coefficient; θ is the rotational angle of the cleaning medium supply member; h is the vertical injection distance between the rotational axis of the cleaning medium supply member and the blade to be cleaned.

8. The self-cleaning fan according to claim 5, wherein, When the self-cleaning blower performs self-cleaning, the cleaning medium supply member rotates at a uniform speed relative to the volute, and the impeller rotates at a variable speed relative to the volute.

9. The self-cleaning fan according to claim 8, wherein, The rotational speed n of the impeller and the angular velocity ω of the cleaning medium supply member satisfy the relational expression: n = (ωr 2 ) / (hP); where: P is the cleaning coefficient; r and h are the inclined injection distance and the vertical injection distance between the rotational axis of the cleaning medium supply member and the blade to be cleaned, respectively.

10. Range hood, characterized in that, Comprising: A housing; And The self-cleaning blower according to any one of claims 1 to 9, the blower main body of the self-cleaning blower is disposed within the housing.

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