CN221442878U - Fan and cleaning equipment - Google Patents
Fan and cleaning equipment Download PDFInfo
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- CN221442878U CN221442878U CN202420265148.7U CN202420265148U CN221442878U CN 221442878 U CN221442878 U CN 221442878U CN 202420265148 U CN202420265148 U CN 202420265148U CN 221442878 U CN221442878 U CN 221442878U
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- 238000004140 cleaning Methods 0.000 title claims abstract description 16
- 230000001965 increasing effect Effects 0.000 claims abstract description 16
- 238000010992 reflux Methods 0.000 claims abstract description 8
- 230000006835 compression Effects 0.000 abstract description 15
- 238000007906 compression Methods 0.000 abstract description 15
- 239000000428 dust Substances 0.000 description 10
- 230000000694 effects Effects 0.000 description 7
- 230000001939 inductive effect Effects 0.000 description 4
- 230000009286 beneficial effect Effects 0.000 description 3
- 230000006698 induction Effects 0.000 description 3
- 238000010408 sweeping Methods 0.000 description 3
- 230000002349 favourable effect Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000001914 filtration Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
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Abstract
The utility model discloses a fan and cleaning equipment, and relates to the technical field of fans. The fan comprises a shell, a first impeller, a second impeller, a driving device and a reflux device, wherein the shell is provided with a first air inlet, a first air outlet, a first cavity and a second cavity, and due to the fact that the scheme that the first impeller and the second impeller suck air jointly is adopted, primary compression is completed when air flow passes through the first impeller, secondary compression is completed after the air flow passes through the second impeller, and therefore the fan can obtain higher vacuum degree and larger suction after secondary compression. The first impeller and the second impeller do not need to adopt higher rotating speed, so that noise can be ensured not to be obviously increased, mechanical loss can be reduced under low rotating speed, and meanwhile, under the guidance of the induced air channel of the reflux device, pneumatic loss can be reduced, and further, the working efficiency of the fan is improved.
Description
Technical Field
The utility model relates to the technical field of fans, in particular to a fan and cleaning equipment.
Background
Cleaning equipment such as a sweeping robot, a dust collector and the like is provided with a volute fan for sucking air, and the volute fan can be used for sucking dust, hair and the like after generating suction force by taking the dust collector as an example, and the size of the suction force influences the cleaning effect of the dust collector. In the related art, in order to obtain high vacuum degree and large suction force, a plurality of impellers are adopted to increase the vacuum degree and the suction force, but the trend of the air flow is unreasonable in design, so that the air flow loss is large easily caused, and the working efficiency is low.
Disclosure of utility model
The present utility model aims to solve at least one of the technical problems existing in the prior art. Therefore, the utility model provides the fan, which can reduce the air flow loss and improve the efficiency of the fan.
The utility model further provides cleaning equipment with the fan.
According to an embodiment of the first aspect of the present utility model, a fan includes:
The shell is provided with a first air inlet, a first cavity, a first air passing opening, a second cavity and a first air outlet which are communicated in sequence;
the first impeller is rotationally arranged in the first cavity;
the second impeller is rotationally arranged in the second cavity;
a driving device in driving connection with the first impeller and the second impeller;
And the reflux device is arranged in the first cavity and positioned between the first impeller and the second impeller, and is provided with an induced air channel used for guiding air flow generated by the first impeller to the second impeller.
The fan provided by the embodiment of the utility model has at least the following beneficial effects:
Through setting up first impeller and second impeller and rotating under drive arrangement's drive, can inhale first cavity with the air current from the first air intake of shell, then pass through induced air passageway, first air gap and the second cavity of backward flow ware in proper order, blow out from first air outlet at last. Because the scheme of common suction of the first impeller and the second impeller is adopted, the air flow completes the first-stage compression when passing through the first impeller, and completes the second-stage compression after passing through the second impeller, so that the fan can obtain higher vacuum degree and higher suction after passing through the two-stage compression. And the first impeller and the second impeller do not need to adopt higher rotating speed, so that the noise can be ensured not to be obviously increased, and the mechanical loss can be reduced at low rotating speed. Simultaneously, because the first impeller is radially air-out, the air flow is easy to directly strike the side wall of the first cavity, the air flow is disturbed, and the air flow loss is large, so that the air flow is guided to flow towards the second impeller by arranging the induced air channel, the pneumatic loss is reduced, and the working efficiency of the fan is further improved.
According to some embodiments of the utility model, the air return device comprises an air guide seat and a plurality of guide vanes, wherein the guide vanes are connected to one side of the air guide seat, which is away from the first impeller, and are arranged at intervals along the circumferential direction of the rotation axis of the first impeller, and the air guide channels are formed between the adjacent guide vanes.
According to some embodiments of the utility model, a side of the air guiding seat facing away from the first impeller protrudes towards the first air passing opening.
According to some embodiments of the utility model, the plurality of guide vanes are connected to the bottom wall of the first cavity, and the bottom wall of the first cavity is disposed obliquely toward the first air passing opening.
According to some embodiments of the utility model, a side wall of the first cavity is provided with a diversion cambered surface, and the diversion cambered surface is concavely arranged along a direction away from the first impeller and extends to an air inlet end of the induced air channel.
According to some embodiments of the utility model, the first impeller comprises a first ring plate and a plurality of first blades connected to the first ring plate, the plurality of first blades being circumferentially spaced along the rotational axis of the first impeller, the projection of the first blades being located between the inner and outer contours of the projection of the first ring plate on a projection plane perpendicular to the rotational axis of the first impeller.
According to some embodiments of the utility model, the second impeller comprises a second ring plate and a plurality of second blades connected to the second ring plate, the plurality of second blades are arranged at intervals along the circumference of the rotation axis of the second impeller, and on a projection plane perpendicular to the rotation axis of the second impeller, the projection of the second blades protrudes out of the inner contour projected by the second ring plate.
According to some embodiments of the utility model, the first impeller comprises a plurality of first blades circumferentially spaced along the rotational axis of the first impeller, and the second impeller comprises a plurality of second blades circumferentially spaced along the rotational axis of the second impeller, the number of second blades being greater than the number of first blades.
According to some embodiments of the utility model, along the axial direction of the first impeller, the maximum height of the first blade towards the end of the rotation axis of the first impeller is H 1, and the maximum height of the second blade towards the end of the rotation axis of the second impeller is H 2, satisfying: 0.6 h 1≤H2≤0.9*H1.
According to some embodiments of the utility model, along the axial direction of the first impeller, the lowest height of the end of the first blade facing away from the rotation axis of the first impeller is H 3, and the lowest height of the end of the second blade facing away from the rotation axis of the second impeller is H 4, so that: 0.8 h 3≤H4＜H3.
According to some embodiments of the utility model, the first impeller comprises a plurality of first blades which are arranged at intervals along the circumferential direction of the rotation axis of the first impeller, a second air outlet is formed between two adjacent first blades, the second air outlet is positioned at one end which is away from the rotation axis of the first impeller, the second impeller comprises a plurality of second blades which are arranged at intervals along the circumferential direction of the rotation axis of the second impeller, a third air outlet is formed between two adjacent second blades, the third air outlet is positioned at one end which is away from the rotation axis of the second impeller, and the air outlet cross section area of the third air outlet is smaller than the air outlet cross section area of the second air outlet.
According to some embodiments of the utility model, the first impeller comprises a first annular plate and a plurality of first blades connected to the first annular plate, the plurality of first blades are arranged at intervals along the circumferential direction of the rotation axis of the first impeller, the first annular plate is provided with a first through hole for air intake, the second impeller comprises a second annular plate and a plurality of second blades connected to the second annular plate, the plurality of second blades are arranged at intervals along the circumferential direction of the rotation axis of the second impeller, the second annular plate is provided with a second through hole for air intake, and the minimum inner diameter of the first through hole is larger than the minimum inner diameter of the second through hole.
According to some embodiments of the utility model, a second air passing port communicated with the first air passing port is arranged on one side, facing the first air passing port, of the reflux device, the minimum inner diameter of the second air passing port is D 1, a second through hole for air inlet is arranged on the second impeller, the minimum inner diameter of the second through hole is D 2, and the requirements are met: -2mm < D 1-D2 < 2mm.
According to some embodiments of the utility model, the housing comprises an air inlet housing and an air outlet volute connected, wherein the air inlet housing is formed with the first cavity, and the air outlet volute is formed with the second cavity.
According to some embodiments of the utility model, an air outlet channel is formed in the air outlet volute, a part of the bottom wall of the air outlet volute is recessed along the direction away from the second impeller to form a groove, and the groove is arranged around the second impeller and forms a part of the structure of the air outlet channel.
According to some embodiments of the utility model, the air outlet cross-sectional area of the air outlet channel gradually increases along the air outlet direction of the air outlet channel.
A cleaning device according to an embodiment of the second aspect of the utility model comprises a blower as described in the above embodiments.
The cleaning device provided by the embodiment of the utility model has at least the following beneficial effects:
Through setting up first impeller and second impeller and rotating under drive arrangement's drive, can inhale first cavity with the air current from the first air intake of shell, then pass through induced air passageway, first air gap and the second cavity of backward flow ware in proper order, blow out from first air outlet at last. Because the scheme of common suction of the first impeller and the second impeller is adopted, the air flow completes the first-stage compression when passing through the first impeller, and completes the second-stage compression after passing through the second impeller, so that the fan can obtain higher vacuum degree and higher suction after passing through the two-stage compression. And the first impeller and the second impeller do not need to adopt higher rotating speed, so that the noise can be ensured not to be obviously increased, and the mechanical loss can be reduced at low rotating speed. Simultaneously, because the first impeller is radially air-out, the air flow is easy to directly strike the side wall of the first cavity, the air flow is disturbed, and the air flow loss is large, so that the air flow is guided to flow towards the second impeller by arranging the induced air channel, the pneumatic loss is reduced, and the working efficiency of the fan is further improved.
Additional aspects and advantages of the utility model will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the utility model.
Drawings
The utility model is further described with reference to the accompanying drawings and examples, in which:
FIG. 1 is a schematic view of a blower according to an embodiment of the utility model;
FIG. 2 is a schematic diagram of a fan in accordance with another aspect of an embodiment of the present utility model;
FIG. 3 is an exploded view of a blower according to one embodiment of the utility model;
FIG. 4 is a cross-sectional view of a blower of one embodiment of the utility model;
FIG. 5 is a cross-sectional view of an air intake housing and a return of an embodiment of the present utility model;
FIG. 6 is a top view of a first impeller according to an embodiment of the present utility model;
FIG. 7 is a schematic view of the construction of a second impeller in accordance with an embodiment of the present utility model;
FIG. 8 is a top view of a second impeller according to an embodiment of the present utility model;
FIG. 9 is a cross-sectional view of a first impeller of an embodiment of the present utility model;
FIG. 10 is a cross-sectional view of a second impeller of an embodiment of the present utility model;
FIG. 11 is an exploded view of an outlet volute of one embodiment of the present utility model;
FIG. 12 is a side view of a blower of one embodiment of the utility model;
Fig. 13 is a cross-sectional view at A-A in fig. 12.
Reference numerals:
a blower 1000;
A housing 100; an air intake housing 110; a first air inlet 111; a first cavity 112; a diversion cambered surface 113; an air-out volute 120; a second cavity 121; a first air outlet 122; an air outlet passage 123; a mounting base 124; an upper shell portion 125; a lower shell portion 126; a groove 127; a first air port 130;
A first impeller 200; a first ring plate 210; a first through hole 211; a first blade 220; first channel 221 first floor 230; a second air inlet 240; a second air outlet 250; a first mounting portion 260;
A second impeller 300; a second ring plate 310; a second through hole 311; a second blade 320; a second channel 321; a second bottom plate 330; a third air inlet 340; a third air outlet 350; a second mounting portion 360;
A reflow apparatus 400; a guide vane 410; an induced draft channel 420; a second air port 430; an air guide seat 440;
A rotation shaft 500.
Detailed Description
Embodiments of the present utility model are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are illustrative only and are not to be construed as limiting the utility model.
In the description of the present utility model, it should be understood that references to orientation descriptions such as upper, lower, front, rear, left, right, etc. are based on the orientation or positional relationship shown in the drawings, are merely for convenience of description of the present utility model and to simplify the description, and do not indicate or imply that the apparatus or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus should not be construed as limiting the present utility model.
In the description of the present utility model, a number means one or more, a number means two or more, and greater than, less than, exceeding, etc. are understood to not include the present number, and above, below, within, etc. are understood to include the present number. The description of the first and second is for the purpose of distinguishing between technical features only and should not be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated or implicitly indicating the precedence of the technical features indicated.
In the description of the present utility model, unless explicitly defined otherwise, terms such as arrangement, installation, connection, etc. should be construed broadly and the specific meaning of the terms in the present utility model can be reasonably determined by a person skilled in the art in combination with the specific contents of the technical scheme.
Referring to fig. 1 and 2, a blower 1000 according to an embodiment of the present utility model may be used in a cleaning apparatus such as a cleaner, a sweeping robot, etc. The fan 1000 includes a housing 100, a first impeller 200, a first air inlet 111 and a first air outlet 122, where the first air inlet 111 and the first air outlet 122 are both disposed on the housing 100, and the first impeller 200 is disposed inside the housing 100. By driving the first impeller 200 to rotate, the air flow can enter the housing 100 from the first air inlet 111 and finally be blown out from the first air outlet 122.
In order to enable the blower 1000 to obtain a higher vacuum and a greater suction force, and to ensure that the noise does not increase significantly, referring to fig. 3 and 4, in the embodiment of the present utility model, the blower 1000 further includes a second impeller 300, a driving device, not shown in the drawing, and a return 400. The housing 100 is further provided with a first cavity 112, a second cavity 121 and a first air port 130, and the first air port 130 is located between the first cavity 112 and the second cavity 121. The first impeller 200 is disposed in the first cavity 112, the second impeller 300 is disposed in the second cavity 121, the driving device is connected to the first impeller 200 and the second impeller 300 through the rotation shaft 500, and the first air inlet 111, the first cavity 112, the first air outlet 130, the second cavity 121 and the first air outlet 122 are sequentially communicated.
Referring to fig. 5, a return 400 is provided in the first chamber 112 between the first impeller 200 and the second impeller 300, and the return 400 is provided with an induced draft channel 420 for guiding the air flow generated by the first impeller 200 to the second impeller 300. When the driving device drives the first impeller 200 and the second impeller 300 to rotate along the same direction, the air flow enters from the first air inlet 111, then sequentially passes through the first cavity 112, the air inducing channel 420, the first air passing port 130 and the second cavity 121, and finally is blown out from the first air outlet 122.
Because the scheme of co-sucking the first impeller 200 and the second impeller 300 is adopted, the air flow completes the first-stage compression when passing through the first impeller 200, and completes the second-stage compression after passing through the second impeller 300, so that the fan 1000 obtains higher vacuum degree and larger suction after passing through the two-stage compression. The first impeller 200 and the second impeller 300 do not need to use higher rotational speeds, can ensure that noise does not increase significantly, and can reduce mechanical losses at low rotational speeds. Meanwhile, the first impeller 200 is capable of exhausting air in the radial direction, so that air flow is easy to directly strike on the side wall of the first cavity 112, and air flow is disturbed, and air flow loss is large. Therefore, the induced air channel 420 is provided to guide the air flow to flow towards the second impeller 300, so as to reduce the pneumatic loss and further improve the working efficiency of the fan 1000.
Referring to fig. 5 and 13, in the embodiment of the present utility model, the air reflector 400 includes an air guiding seat 440 and a plurality of guide vanes 410, the plurality of guide vanes 410 are connected to a side of the air guiding seat 440 facing away from the first impeller 200, the plurality of guide vanes 410 are circumferentially spaced along the rotation axis of the first impeller 200, and an air guiding channel 420 is formed between adjacent guide vanes 410, i.e. the air guiding channel 420 is provided with a plurality of air guiding channels. The plurality of air induction channels 420 are also arranged at intervals along the circumferential direction of the rotation axis of the first impeller 200, so that the air flow direction can be guided in a plurality of directions, thereby improving the uniformity of the air outlet.
Referring to fig. 4, in the embodiment of the present utility model, a side of the air guiding seat 440 facing away from the first impeller 200 protrudes toward the first air passing opening 130, which is favorable for guiding the air flow coming out of the air guiding channel 420 to flow toward the first air passing opening 130, so that the air flow direction is smoother, the air flow loss caused by air flow turbulence is effectively reduced, and the working efficiency of the fan 1000 can be improved.
With continued reference to fig. 4, in an embodiment of the present utility model, a plurality of guide vanes are connected to a bottom wall of the first cavity, and the bottom wall of the first cavity is disposed obliquely toward the first air passing opening. Accordingly, the upper end of the induced draft channel 420 extends toward the first impeller 200, and the lower end of the induced draft channel 420 extends toward the first air passing opening 130. Or, along the air inlet direction of the air inducing channel 420, the included angle between the air inducing channel 420 and the axis of the rotating shaft 500 is gradually reduced, which is favorable for guiding the air flow to pass through the first air passing port 130 and then enter the second through hole 311 of the second impeller 300, further reducing the air flow loss and improving the efficiency of the fan 1000.
Referring to fig. 13, in the embodiment of the present utility model, the air induction channels 420 are arc-shaped, and the plurality of air induction channels 420 are distributed in a vortex shape. Because the air flow generated by the first impeller 200 rotates along the side wall of the first cavity 112, the air guide channel is arc-shaped and is in vortex-shaped distribution, so that the trend of the air flow can be better guided, the deflection of the air flow is realized, the air flow flows to the second impeller 300 according to a set angle, and the problem of air flow disorder caused by inconsistent air flow direction and the direction of the third air inlet 340 is effectively avoided.
Referring to fig. 4 and 5, in the embodiment of the present utility model, a second air passing hole 430 communicating with the first air passing hole 130 is provided at a side of the return 400 facing the first air passing hole 130, the minimum inner diameter of the second air passing hole 430 is D 1, and the minimum inner diameter of the second through hole 311 of the second impeller 300 is D 2, so that: 2 mm.ltoreq.D 1-D2.ltoreq.2 mm, for example D 1 and D 2 may be equal. When D 1-D2 is smaller than-2 mm, the air-out sectional area of the second air-passing opening 430 is too small, and the air-out efficiency is low. When D 1-D2 is greater than 2mm, the air-out sectional area of the second air-passing opening 430 is too large, resulting in a part of the air flow striking the inner wall of the housing 100, causing turbulence of the air flow. Therefore, by designing-2 mm < D 1-D2 < 2mm, most of the air flow guided by the reflux device 400 smoothly enters the second impeller 300, the air inlet efficiency can be improved, and the occurrence of air flow disturbance can be effectively reduced.
Referring to fig. 4, in the embodiment of the present utility model, a side wall of the first cavity 112 is provided with a diversion cambered surface 113, and the diversion cambered surface 113 is concavely disposed along a direction away from the first impeller 200 and extends to an air inlet end of the air inducing channel 420. Because the first impeller 200 is a centrifugal wind wheel, the air flow can be thrown out along the radial direction of the first impeller, and therefore, the diversion cambered surface 113 is arranged on the side wall of the first cavity 112, so that the air flow is guided into the induced air channel 420, the air flow loss can be effectively reduced, and the working efficiency of the fan 1000 is improved.
Referring to fig. 3, in the embodiment of the present utility model, the first impeller 200 includes a first ring plate 210, first blades 220 and a first base plate 230, the first ring plate 210 and the first base plate 230 are disposed at intervals along an axial direction of the first impeller 200, the first blades 220 are provided in plurality and are connected between the first ring plate 210 and the first base plate 230, and the plurality of first blades 220 are disposed at intervals around a rotation axis of the first impeller 200. The first ring plate 210 is provided with a first through hole 211 for air intake, and a first channel 221 for air outlet is formed between adjacent first blades 220. The first impeller 200 is a centrifugal impeller, that is, the first impeller 200 can intake air in the axial direction and discharge air in the radial direction. When the first impeller 200 rotates, the air flow can enter from the first through hole 211, then be blown out to the side wall of the first cavity 112 through the first channel 221, and then be blown toward the second impeller 300 under the guidance of the induced air channel 420 of the backflow unit 400. Compared with the scheme of an axial flow wind wheel, the centrifugal impeller can generate higher wind pressure, has higher efficiency and can improve the air suction effect.
Referring to fig. 6, in the embodiment of the present utility model, the dotted line in fig. 6 represents the contour of the first blade 220 blocked by the first ring plate 210. On a projection plane perpendicular to the rotation axis of the first impeller 200, the projection profile of the first blade 220 is located between the inner profile and the outer profile projected by the first ring plate 210. Since no first vane 220 is blocked at the first through hole 211, the air inlet area of the first impeller 200 can be increased, the air inlet efficiency is improved, the manufacturability is better, and the production difficulty is low.
Referring to fig. 7, in the embodiment of the present utility model, the second impeller 300 includes a second ring plate 310, second blades 320 and a second base plate 330, the second ring plate 310 and the second base plate 330 are spaced apart along the axial direction of the second impeller 300, the second blades 320 are provided in plurality and connected between the second ring plate 310 and the second base plate 330, and the plurality of second blades 320 are spaced apart around the rotation axis of the second impeller 300. The second ring plate 310 is provided with second through holes 311 for air intake, and second passages 321 are formed between adjacent second blades 320. The second impeller 300 is a centrifugal impeller, that is, the second impeller 300 can intake air in the axial direction and discharge air in the radial direction. When the second impeller 300 rotates, the air flow can enter from the second through hole 311, then be blown out to the side wall of the second cavity 121 through the second channel 321, and finally be blown out from the first air outlet 122.
Referring to fig. 7 and 8, in the embodiment of the present utility model, on a projection plane perpendicular to the rotation axis of the second impeller 300, the projection contour of the second blade 320 protrudes from the inner contour projected by the second ring plate 310 toward one side of the rotation axis of the second impeller 300. The purpose is to increase the contact area between the blade and the air flow and improve the capability of acting on the air flow. While the cross-sectional area of the second passage 321 may be reduced to increase the flow rate of the air flow and increase the suction force. When the fan 1000 is applied to the inside of the cleaner, the negative pressure effect in the inside of the cleaner can be effectively increased, thereby improving the suction force and the dust collection efficiency of the cleaner. In the following embodiments, the fan 1000 is used in the dust collector as an example, unless otherwise specified.
Therefore, the reason why the structure of the first impeller 200 is different from that of the second impeller 300 is that the functions are different, and the first impeller 200 is intended to achieve a larger intake air quantity while being convenient to manufacture. After the airflow is boosted by the first impeller 200, the second impeller 300 is required to do further work on the airflow, so as to further increase the speed of the airflow. Therefore, the second impeller 300 may design that one end of the second blade 320 facing the rotation axis of the second impeller 300 protrudes out of the second through hole 311, so as to increase the contact area with the air flow, improve the work-doing capability on the air flow and further increase the air flow velocity.
Referring to fig. 6 and 8, in the embodiment of the present utility model, the number of the first blades 220 is less than the number of the second blades 320. For example, the number of the first blades 220 is 9, and the number of the second blades 320 is 13. Of course, the number of the first blades 220 and the second blades 320 may be other numbers, for example, the number of the first blades 220 is 7, and the number of the second blades 320 is 11, and the number is selected as appropriate according to practical situations. It will be appreciated that since the number of second blades 320 is greater than the number of first blades 220, the cross-sectional area of the first channel 221 is greater than the cross-sectional area of the second channel 321 in the case where the maximum outer diameter of the first impeller 200 and the maximum outer diameter of the second impeller 300 are the same. The cross-sectional area refers to the area of the cross-section that is generated when the first impeller 200 and the second impeller 300 are coaxially disposed and the first passage 221 and the second passage 321 are cut by a section plane parallel to the rotation axis of the first impeller 200. Because the cross-sectional area of the second channel 321 is small, the flow velocity of the air is faster than that of the first channel 221, and the contact area between the second blades 320 and the air flow can be further increased, so that the working efficiency of the air flow is improved, the negative pressure effect inside the dust collector is effectively increased, and the suction force of the dust collector is improved.
Referring to fig. 9 and 10, in the embodiment of the present utility model, along the axial direction of the first impeller 200, the maximum height of the first vane 220 toward the end of the rotation axis of the first impeller 200 is H 1, and the maximum height of the second vane 320 toward the end of the rotation axis of the second vane 320 is H 2, satisfying: 0.6H 1≤H2≤0.9*H1, this formula is equivalent to 0.6.ltoreq.h 2/H1.ltoreq.0.9, for example, as H 2/H1＝0.7、H2/H1 =0.75 or H 2/H1 =0.8. The maximum height of the first vane 220 refers to: the first vane 220 is directed toward one end of the rotation axis of the first impeller 200 and is connected to a height between the highest point of the first ring plate 210 and the first bottom plate 230; the maximum height of the second vane 320 refers to: the second vane 320 is directed toward one end of the rotation axis of the second impeller 300 and is connected to a height between the highest point of the second ring plate 310 and the second base plate 330.
The end of the first channel 221 facing the rotation axis of the first impeller 200 is a second air inlet 240, and the end of the second channel 321 facing the rotation axis of the second impeller 300 is a third air inlet 340. The height may affect the size of the air intake area, and when H 2/H1 is less than 0.6, the height of the second blade 320 is too low, and the air intake area of the third air intake 340 is too small, which may easily cause air intake blockage, efficiency reduction, and noise and vibration increase. When H 2/H1 is greater than 0.9, although the air intake efficiency can be improved, it is difficult to achieve an effect of increasing the wind speed. Therefore, by reasonably designing the relationship between H 1 and H 2, the air inlet area of the third air inlet 340 is smaller than the air inlet area of the second air inlet 240, so that the air speed can be increased while ensuring a certain air inlet efficiency.
With continued reference to fig. 9, in the embodiment of the present utility model, along the axial direction of the first impeller 200, the lowest height of the end of the first blade 220 facing away from the rotation axis of the first impeller 200 is H 3, and the lowest height of the end of the second blade 320 facing away from the rotation axis of the second impeller 300 is H 4, so that: 0.8H 3≤H4＜H3, this formula equates to 0.8 +.h 4/H3 < 1, e.g. H 4/H3＝0.85、H4/H3 =0.9 or H 4/H3 =0.95. Note that, the lowest height of the first blade 220 refers to: the first vane 220 is directed away from one end of the rotation axis of the first impeller 200 and is connected to a height between the lowest point of the first ring plate 210 and the first bottom plate 230; the lowest height of the second vane 320 refers to: the second vane 320 is directed away from one end of the rotation axis of the second impeller 300 and is connected to a height between the lowest point of the second ring plate 310 and the second bottom plate 330.
The end of the first channel 221 facing away from the rotation axis of the first impeller 200 is the second air outlet 250, and the end of the second channel 321 facing away from the rotation axis of the second impeller 300 is the third air outlet 350. When H 4/H3 is less than 0.8, the air-out cross-sectional area of the third air outlet 350 is too small, which easily results in reduced air-out efficiency, and increased noise and vibration. When H 4/H3 is 1 or more, it is difficult to exert an effect of increasing the wind speed. Therefore, by reasonably designing the relationship between H 3 and H 4, the air-out cross-sectional area of the third air outlet 350 is smaller than the air-out cross-sectional area of the second air outlet 250, so that the air-out efficiency can be ensured and the air-out speed can be increased.
Referring to fig. 6 and 8, in the embodiment of the present utility model, the minimum inner diameter of the first through hole 211 is larger than the minimum inner diameter of the second through hole 311. It will be appreciated that the smallest inner diameters of the first through hole 211 and the second through hole 311 reflect the size of the air intake area, i.e. the air intake area of the first through hole 211 is larger than the air intake area of the second through hole 311. Since the first impeller 200 mainly ensures a large air intake, the second impeller 300 mainly plays a role in improving the air flow speed, so that the first impeller 200 can ensure a large air intake by designing that D 1 is larger than D 2, and the second impeller 300 can increase the air flow speed by reducing the air intake area.
Referring to fig. 3 and 4, in the embodiment of the present utility model, the housing 100 includes an air inlet housing 110 and an air outlet volute 120, the air inlet housing 110 is connected to the air outlet volute 120, the air inlet housing 110 is provided with a first cavity 112 and a first air inlet 111, and the air outlet volute 120 is provided with a second cavity 121 and a first air outlet 122. By adopting the scheme of the air outlet volute 120, the air outlet direction of the second impeller 300 can be adapted, and the efficiency and performance of the fan 1000 can be improved.
Referring to fig. 11 and 12, in an embodiment of the present utility model, the outlet volute 120 includes an upper casing portion 125 and a lower casing portion 126, the upper casing portion 125 and the lower casing portion 126 are connected, and a second cavity 121 is defined between the upper casing portion 125 and the lower casing portion 126. The air-out scroll 120 is formed with an air-out passage 123, and a portion of the bottom wall of the lower casing portion 126 is concavely formed with a groove 127 in a direction away from the second impeller 300, and the groove 127 is disposed around the second impeller 300 and formed as a portion of the structure of the air-out passage 123, along which air flow can be blown out, for example, in a direction of a dotted arrow in fig. 11.
It will be appreciated that the cross-sectional area of the outlet volute 120 during outlet air should meet certain requirements, and should not be too large or too small, which may cause turbulence in the air flow, and too small, which may cause blockage, resulting in reduced efficiency. In order to make the outlet cross-sectional area of the outlet air passage 123 satisfactory, the groove 127 is protruded in the radial direction of the second impeller 300 or protruded in a direction away from the second impeller 300. When the groove 127 protrudes in the radial direction of the second impeller 300, an increase in the size of the blower 1000 in the radial direction may be caused, which is disadvantageous in downsizing of the blower 1000. And when the groove 127 protrudes along the direction deviating from the second impeller 300, since the bottom wall of the air outlet volute 120 is also required to be provided with a driving device, the driving device can occupy a certain position in the axial direction, so that the length of the fan 1000 in the axial direction cannot be increased by the scheme of the embodiment, the miniaturization of the fan 1000 is facilitated, and the space occupied by the fan 1000 is reduced.
Referring to fig. 11 and 12, in the embodiment of the present utility model, the air outlet cross-sectional area of the air outlet channel 123 gradually increases along the air outlet direction of the air outlet channel 123. The air outlet speed can be slowed down so that the air pressure of the air outlet passage 123 increases. When the air pressure is increased, the suction force of the dust collector can be further improved, so that the air flow can pass through a pipeline and a filtering system of the dust collector, and the cleaning effect is improved.
As can be seen from the above, the first impeller 200 mainly ensures that the fan 1000 has a larger air intake; the reflux 400 plays a role in guiding the air flow direction, so that the air flow loss is reduced; the second impeller 300 can further increase the speed of the air flow; the air outlet channel 123 can further increase the pressure of the air flow, so that the fan 1000 obtains higher vacuum degree and higher suction force.
Referring to fig. 2, in the embodiment of the present utility model, the driving device includes a motor, not shown in the motor, the bottom of the air outlet volute 120 is provided with a mounting seat 124, and the motor is fixedly connected with the mounting seat 124 and is in driving connection with the rotating shaft 500, so that the motor can drive the first impeller 200 and the second impeller 300 to rotate synchronously through the rotating shaft 500. In another embodiment of the present utility model, the driving device may further include two motors, through which the first impeller 200 and the second impeller 300 are driven to rotate, respectively, and an appropriate scheme is selected according to practical situations.
Referring to fig. 9 and 10, in the embodiment of the present utility model, the first base plate 230 is provided with a first mounting portion 260, and the second base plate 330 is provided with a second mounting portion 360, and the first mounting portion 260 and the second mounting portion 360 are fixedly coupled with the rotation shaft 500. Since the first mounting portion 260 is cylindrical, the first mounting portion 260 has high overall strength, and can ensure the stability of the connection with the rotation shaft 500. The outer wall of the second mounting part 360 is tapered, and since the second impeller 300 is positioned between the first impeller 200 and the motor and is connected to the middle position of the rotation shaft 500, the strength requirement is low with respect to the first mounting part 260, and thus the second impeller is designed to be tapered to reduce air flow loss and improve the efficiency of the blower 1000.
The cleaning device according to an embodiment of the present utility model includes the blower 1000 according to the above embodiment, and the cleaning device may be a cleaner or a sweeping robot. The cleaning apparatus according to the embodiment of the present utility model adopts the blower 1000 of the foregoing embodiment, and by setting the first impeller 200 and the second impeller 300 to rotate under the driving of the driving device, the air flow can be sucked into the first cavity 112 from the first air inlet 111 of the housing 100, then sequentially passes through the air guiding channel 420, the first air passing port 130 and the second cavity 121 of the reflow apparatus 400, and finally is blown out from the first air outlet 122. Because the scheme of co-sucking the first impeller 200 and the second impeller 300 is adopted, the air flow completes the first-stage compression when passing through the first impeller 200, and completes the second-stage compression after passing through the second impeller 300, so that the fan 1000 obtains higher vacuum degree and larger suction after passing through the two-stage compression. And the first impeller 200 and the second impeller 300 do not need to adopt higher rotation speed, so that noise can be ensured not to be obviously increased, mechanical loss can be reduced at low rotation speed, and meanwhile, under the guidance of the induced air channel 420, pneumatic loss can be reduced, and further, the working efficiency of the fan 1000 is improved.
Since the cleaning device adopts all the technical solutions of the blower 1000 in the foregoing embodiments, at least all the beneficial effects brought by the technical solutions in the foregoing embodiments are not described herein.
The embodiments of the present utility model have been described in detail with reference to the accompanying drawings, but the present utility model is not limited to the above embodiments, and various changes can be made within the knowledge of one of ordinary skill in the art without departing from the spirit of the present utility model.
Claims (17)
1. The fan, its characterized in that: comprising the following steps:
The shell is provided with a first air inlet, a first cavity, a first air passing opening, a second cavity and a first air outlet which are communicated in sequence;
the first impeller is rotationally arranged in the first cavity;
the second impeller is rotationally arranged in the second cavity;
a driving device in driving connection with the first impeller and the second impeller;
And the reflux device is arranged in the first cavity and positioned between the first impeller and the second impeller, and is provided with an induced air channel used for guiding air flow generated by the first impeller to the second impeller.
2. The fan of claim 1, wherein the air return device comprises an air guide seat and a plurality of guide vanes, the guide vanes are connected to one side of the air guide seat away from the first impeller and are arranged at intervals along the circumferential direction of the rotation axis of the first impeller, and the air guide channels are formed between the adjacent guide vanes.
3. The fan of claim 2, wherein a side of the air guide seat facing away from the first impeller protrudes toward the first air passage.
4. The fan of claim 2, wherein a plurality of said guide vanes are connected to the bottom wall of said first cavity, and the bottom wall of said first cavity is disposed obliquely toward said first air port.
5. The fan of claim 1, wherein a side wall of the first cavity is provided with a diversion cambered surface, and the diversion cambered surface is concavely arranged along a direction away from the first impeller and extends to an air inlet end of the induced air channel.
6. The fan of claim 1, wherein the first impeller comprises a first ring plate and a plurality of first blades coupled to the first ring plate, the plurality of first blades being circumferentially spaced along the axis of rotation of the first impeller, the projection of the first blades being located between the inner and outer contours of the projection of the first ring plate on a projection plane perpendicular to the axis of rotation of the first impeller.
7. The fan of claim 1 or 6, wherein the second impeller comprises a second ring plate and a plurality of second blades connected to the second ring plate, the plurality of second blades being circumferentially spaced along the axis of rotation of the second impeller, and wherein the projections of the second blades project from the inner contour of the projection of the second ring plate on a projection plane perpendicular to the axis of rotation of the second impeller.
8. The fan of claim 1, wherein the first impeller includes a plurality of first blades circumferentially spaced along the rotational axis of the first impeller, and the second impeller includes a plurality of second blades circumferentially spaced along the rotational axis of the second impeller, the number of second blades being greater than the number of first blades.
9. The wind turbine of claim 8, wherein the maximum height of the first blade toward the end of the rotational axis of the first impeller is H 1 and the maximum height of the second blade toward the end of the rotational axis of the second impeller is H 2 in the axial direction of the first impeller, satisfying: 0.6 h 1≤H2≤0.9*H1.
10. The fan of claim 8, wherein the first blade has a minimum height H 3 at an end facing away from the rotational axis of the first impeller and a minimum height H 4 at an end facing away from the rotational axis of the second impeller in the axial direction of the first impeller, satisfying: 0.8 h 3≤H4＜H3.
11. The fan of claim 1, wherein the first impeller comprises a plurality of first blades arranged at intervals along the circumferential direction of the rotation axis of the first impeller, a second air outlet is formed between two adjacent first blades, the second air outlet is positioned at one end of the first blades, which is away from the rotation axis of the first impeller, the second impeller comprises a plurality of second blades arranged at intervals along the circumferential direction of the rotation axis of the second impeller, a third air outlet is formed between two adjacent second blades, the third air outlet is positioned at one end of the second blades, which is away from the rotation axis of the second impeller, and the air outlet cross section area of the third air outlet is smaller than the air outlet cross section area of the second air outlet.
12. The fan of claim 1, wherein the first impeller comprises a first annular plate and a plurality of first blades connected to the first annular plate, the plurality of first blades are arranged at intervals along the circumference of the rotation axis of the first impeller, the first annular plate is provided with a first through hole for air intake, the second impeller comprises a second annular plate and a plurality of second blades connected to the second annular plate, the plurality of second blades are arranged at intervals along the circumference of the rotation axis of the second impeller, the second annular plate is provided with a second through hole for air intake, and the minimum inner diameter of the first through hole is larger than the minimum inner diameter of the second through hole.
13. The fan according to claim 1, wherein a second air passing port communicated with the first air passing port is arranged on one side, facing the first air passing port, of the reflux device, the minimum inner diameter of the second air passing port is D 1, the second impeller is provided with a second through hole for air intake, and the minimum inner diameter of the second through hole is D 2, so that the requirements are satisfied: -2mm < D 1-D2 < 2mm.
14. The blower of claim 1, wherein the housing includes an inlet housing and an outlet volute connected, the inlet housing defining the first cavity and the outlet volute defining the second cavity.
15. The fan of claim 14, wherein an air outlet channel is formed in the air outlet volute, and a portion of a bottom wall of the air outlet volute is recessed in a direction away from the second impeller to form a groove, and the groove is disposed around the second impeller and is formed as a portion of the air outlet channel.
16. The fan as claimed in claim 15, wherein an outlet cross-sectional area of the outlet passage is gradually increased in an outlet direction of the outlet passage.
17. Cleaning device, its characterized in that: comprising a wind turbine according to any one of claims 1 to 16.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202420265148.7U CN221442878U (en) | 2024-02-02 | 2024-02-02 | Fan and cleaning equipment |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202420265148.7U CN221442878U (en) | 2024-02-02 | 2024-02-02 | Fan and cleaning equipment |
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| Publication Number | Publication Date |
|---|---|
| CN221442878U true CN221442878U (en) | 2024-07-30 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202420265148.7U Active CN221442878U (en) | 2024-02-02 | 2024-02-02 | Fan and cleaning equipment |
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| CN (1) | CN221442878U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2025138873A1 (en) * | 2023-12-25 | 2025-07-03 | 江苏美的清洁电器股份有限公司 | Fan and cleaning apparatus |
-
2024
- 2024-02-02 CN CN202420265148.7U patent/CN221442878U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2025138873A1 (en) * | 2023-12-25 | 2025-07-03 | 江苏美的清洁电器股份有限公司 | Fan and cleaning apparatus |
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