CN215214095U - Backward blade for centrifugal fan impeller, centrifugal fan and range hood - Google Patents
Backward blade for centrifugal fan impeller, centrifugal fan and range hood Download PDFInfo
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- CN215214095U CN215214095U CN202120748012.8U CN202120748012U CN215214095U CN 215214095 U CN215214095 U CN 215214095U CN 202120748012 U CN202120748012 U CN 202120748012U CN 215214095 U CN215214095 U CN 215214095U
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Abstract
The utility model relates to a centrifugal fan impeller is with back to blade, include: a blade body; the first noise reduction structure comprises at least one step formed by sinking from the pressure surface of the blade body to the suction surface, the step is a strip-shaped step extending along the width direction of the pressure surface of the blade body, and each strip-shaped step divides the pressure surface of the blade body into at least two sections of cambered surfaces in the length direction of the pressure surface; the structure of making an uproar falls in second, include from the suction surface of blade body to the convex at least one arch of pressure surface direction of keeping away from, it is protruding for the bar that extends the setting along the width direction of the suction surface of blade body that the arch is protruding, and the bellied surface of each bar is the cylinder. The first noise reduction structure and the second noise reduction structure of the backward blade are designed to effectively block the transverse swing of fluid near the suction surface, so that the boundary layer near the suction surface can be completely distributed, and the boundary layer separation phenomenon is reduced. Still relate to a centrifugal fan and applied this centrifugal fan's range hood.
Description
Technical Field
The utility model relates to a range hood technical field especially relates to centrifugal fan impeller is with back to blade, centrifugal fan and range hood.
Background
The multi-wing centrifugal fan is the main power system of cooking fume exhauster and other ventilation equipment, and has the features of compact structure, low noise, high pressure coefficient, great flow coefficient, etc. Centrifugal fan can be divided into forward type, radial type and backward type according to the blade angle of impeller air outlet end, correspondingly, centrifugal fan's blade divide into forward blade (blade export erection angle is greater than 90 °), radial blade (blade export erection angle equals 90 °) and backward blade (blade export erection angle is less than 90 °). The blade of the centrifugal fan is provided with a pressure surface and a suction surface, wherein the pressure surface of the blade is a working surface, namely the windward surface of the blade; the suction surface of the blade is a non-working surface, namely the leeward surface of the blade. The pressure pulsation, the jet-wake structure, the boundary layer separation and the vortex shedding inside the multi-wing centrifugal fan have great influence on the noise characteristic of the air duct system.
The blade of current impeller mainly adopts single circular arc type line structure, as the impeller for multi-wing centrifugal fan that the chinese utility model patent that application number is 201621179780.1 discloses, the impeller comprises the blade along the circumference equipartition, the impeller external diameter is 180 ~ 240mm, the internal diameter is 150 ~ 180mm, the blade is arc, curvature radius is 18 ~ 25mm, 36 ~ 45 pieces along the circumference equipartition of blade, projection radian theta is 8 ~ 10, blade thickness is 0.8mm ~ 1.2 mm. This greater impeller inlet airflow impingement reduces efficiency while increasing noise.
For another example, chinese patent application No. CN202011087428.6 (publication No. CN112096654A) discloses an impeller, a fan, and a range hood, which optimally designs the profile of the blades of the impeller, and the profile of each blade is a bezier curve, wherein the cross-sectional area of the flow channel formed between two adjacent blades gradually decreases from the inlet of the flow channel to the outlet of the flow channel along the radial direction of the impeller. Although the structure of the impeller reduces the vortex at the inlet of the blade and the flow separation to a certain extent, the air inlet flow is smooth, the flow separation phenomenon of the air flow at the outlet of the blade is also reduced to a certain extent, the flow field condition of the flow channel of the blade is improved, and the purpose of reducing noise is achieved.
For another example, the chinese patent application No. 20141032458. X discloses a bionic impeller for a range hood, which is applied to a range hood, and includes a plurality of sets of annular end surfaces and blades, wherein the blades are bionic blades, and the bionic blades are a leading edge of a waveform structure facing the suction side of the impeller range hood and a trailing edge of a sawtooth structure facing the blowing side of the impeller range hood. The bionic impeller mainly changes the shedding continuity of the trailing edge vortex and reduces the shedding frequency of the trailing edge vortex by reducing the pressure impact of the front edge, thereby reducing the aerodynamic noise.
However, in the above-mentioned multi-blade centrifugal fan, regardless of the optimized design of the profile of the blade or the bionic design of the leading edge and the trailing edge of the blade, it is difficult to effectively solve the problem of separation of the vortices on the pressure surface of the blade in the narrow blade path, and especially, for the problem of lateral swing of the fluid near the suction surface of the blade, the boundary layer is difficult to be completely distributed on the surface of the blade to generate a fault, and the fault of the boundary layer may cause the aerodynamic performance of the blade to be damaged, and generate a large pressure gradient, thereby causing a large noise.
SUMMERY OF THE UTILITY MODEL
The utility model discloses the first technical problem that will solve is to prior art's current situation, provides one kind and can control the rectification to the vortex in the blade way of impeller and the boundary layer separation of air current, and then improves aerodynamic performance, and noise abatement's centrifugal fan impeller is with the back to the blade.
The utility model discloses the second technical problem that will solve is to prior art's current situation, provides the centrifugal fan to the blade after using above-mentioned.
The utility model discloses the third technical problem that will solve is to prior art's current situation, provides a range hood of using above-mentioned centrifugal fan.
The utility model provides a technical scheme that first technical problem adopted does: centrifugal fan is backward blade for impeller includes:
the blade body is integrally arc-shaped and is provided with a first side edge and a second side edge which extend side by side in the length direction, the first side edge is an inlet edge corresponding to inflow of airflow, and the second side edge is an outlet edge corresponding to outflow of the airflow;
the first noise reduction structure comprises at least one step formed by sinking from the pressure surface of the blade body to the suction surface of the blade body, the step is a strip-shaped step extending along the width direction of the pressure surface of the blade body, and the pressure surface of the blade body is divided into at least two sections of cambered surfaces in the length direction of the pressure surface by the strip-shaped steps;
the second noise reduction structure comprises at least one protrusion protruding from the direction of the pressure surface away from the suction surface of the blade body, the protrusion is a strip protrusion extending along the width direction of the suction surface of the blade body, and the surface of each strip protrusion is a cylindrical surface.
As an improvement, the strip-shaped steps are at least two and are sequentially arranged at intervals along the length direction of the blade body, wherein the concave depth of each strip-shaped step is sequentially reduced from the first side edge to the second side edge of the blade body. The purpose of the structural design that the concave depth of the strip-shaped steps on the pressure surface is gradually reduced is as follows: because the vicinity of the front edge of the blade can be impacted by unstable airflow, namely, the pressure fluctuation of a flow field in a strip-shaped step area close to the front edge of the blade is obvious, and the strip-shaped step with larger concave depth can reduce the pressure pulsation of unstable incoming flow; and the strip-shaped step with relatively small concave depth is adopted in the area close to the tail edge of the blade, so that the shock wave intensity of airflow at the outlet of the tail edge of the blade can be greatly reduced.
As an improvement, the strip-shaped protrusions are at least two and are sequentially arranged at intervals along the length direction of the blade body, wherein the protrusion height of each strip-shaped protrusion is sequentially reduced from the first side edge to the second side edge of the blade body. The structure design can reduce the air flow speed near the wall surface of the pressure surface, so that the fluid flows along the wall better.
In order to facilitate machining and reduce machining cost, the number of the strip-shaped steps is two, so that the two strip-shaped steps divide the pressure surface of the blade body into three sections of cambered surfaces, and the number of the strip-shaped protrusions is two correspondingly.
As an improvement, the distance from the first side edge of the blade body to the center of the impeller is r1, the distance from the second side edge of the blade body to the center of the impeller is r2, the three arc surfaces are respectively a first arc surface, a second arc surface and a third arc surface from the first side edge to the second side edge of the blade body, the length of the first arc surface is L1, and the L1 satisfies the condition: l1 is less than or equal to (r2-r 1)/4; the length of the third cambered surface is L3, and L3 meets the condition: l3 is less than or equal to L1 × 3/4.
In order to play a role in stabilizing and smoothing the incoming flow, the better design position of the strip-shaped step is close to the starting point of the front edge of the blade, so that the effects of inhibiting and delaying boundary layer separation are achieved, and separation vortex energy is weakened to a certain extent. The bar step is already difficult to function if the design position of the bar step is relatively back. The other strip-shaped step is designed to be close to the tail edge of the blade, so that the outlet high-pressure airflow close to the tail edge area of the blade has sufficient space for diffusion, the strength of an outlet dipole is reduced, the outlet of a flow channel is smoother, and the total pressure loss is remarkably reduced.
Preferably, the concave depth of the strip-shaped step is h, and h meets the condition: r is1/12＜h＜r1/12+(r2-r1)/15。
As an improvement, an impeller passage is formed between two adjacent blades, the number of the strip-shaped protrusions on the blade body is consistent with the number of the strip-shaped steps, and the strip-shaped protrusions on the suction surface of the previous blade body corresponding to one impeller passage are closer to the center of the impeller than the strip-shaped steps on the pressure surface of the next blade body.
As the horseshoe vortex on the pressure surface side does not change obviously along with the increase of the rotating speed of the fan, the separation vortex moves towards the direction close to the suction surface, the boundary layer on the pressure surface side becomes thinner, the boundary layer on the suction surface becomes thicker, and the strip-shaped convex structure on the suction surface plays a role in pulling the fluid, so that the fluid is changed into a low-speed high-pressure state after passing through the strip-shaped convex, and the static pressure coefficient of the suction surface is increased. The strip-shaped bulges reduce the velocity gradient in the surface area and reduce the turbulence intensity of the cylindrical surface area, thereby reducing the shear stress of the strip-shaped bulges and playing an effective drag reduction role.
The utility model provides a technical scheme that second technical problem adopted does: the utility model provides an use centrifugal fan of above-mentioned back blade, includes the spiral case, locates impeller and motor in the spiral case, the impeller includes back dish and front bezel, the back dish with the front bezel sets up relatively, the back blade locate the back dish with between the front bezel, and follow the circumference interval distribution of front bezel, the power take off end of motor with the back dish drive of impeller is connected.
The utility model provides a technical scheme that third technical problem adopted does: a range hood, this range hood has adopted foretell centrifugal fan.
Compared with the prior art, the utility model has the advantages that: the utility model discloses a centrifugal fan impeller is with being equipped with bar stair structure on the pressure surface to the blade, the protruding structure of bar has on the suction surface, above-mentioned structure setting makes the blade way structure that forms between two adjacent blades obtain optimizing, effectively blocked near fluidic lateral swing of suction surface, make near boundary layer of suction surface can the complete distribution, thereby delay boundary layer separation and restrain near the production secondary flow of suction surface, the fluidic flow state in the blade way has further been improved, make the blade way in fluid speed more even, secondary flow in the blade way, the axial vortex obviously reduces, reduce boundary layer separation phenomenon. When fluid flows through the pressure surface, small vortices are generated in the strip-shaped step structure, and the vortices can enable the boundary layer which should be separated on the pressure surface to be attached to the surface of the blade again, so that the falling of the karman vortex street is inhibited, and a good rectification effect is achieved.
Drawings
Fig. 1 is a schematic perspective view of a range hood according to an embodiment of the present invention;
fig. 2 is a schematic view of a three-dimensional structure of the range hood according to the embodiment of the present invention after the front side plate of the housing is hidden;
fig. 3 is a schematic perspective view of a centrifugal fan of a range hood according to an embodiment of the present invention;
fig. 4 is a vertical cross-sectional view of the centrifugal fan of the range hood according to the embodiment of the present invention;
fig. 5 is a schematic perspective view of an impeller of a centrifugal fan according to an embodiment of the present invention;
fig. 6 is a vertical cross-sectional view of a centrifugal fan impeller according to an embodiment of the present invention;
fig. 7 is a schematic perspective view of a backward blade according to an embodiment of the present invention;
fig. 8 is a pressure and flow line distribution diagram of a suction surface of a blade according to an embodiment of the present invention.
Detailed Description
The present invention will be described in further detail with reference to the following embodiments.
Directional terms such as "front", "rear", "upper", "lower", "left", "right", "side", "top", "bottom", and the like are used in the description and claims of the present invention to describe various example structural portions and elements of the present invention, but these terms are used herein for convenience of description only and are determined based on example orientations shown in the drawings. Because the disclosed embodiments may be arranged in different orientations, these directional terms are for illustrative purposes only and should not be construed as limiting, and for example, "upper" and "lower" are not necessarily limited to orientations opposite or consistent with the direction of gravity.
Referring to fig. 1 to 4, the range hood of the present embodiment includes a housing 50 and a centrifugal fan 40 disposed in the housing 50, where the centrifugal fan 40 includes a volute 41, an impeller 42 and a motor 43, the impeller 42 is disposed in the volute 41, and an output shaft of the motor 43 is connected to the impeller 42 of the centrifugal fan. The centrifugal fan impeller 42 includes a front disk 422, a rear disk 421 disposed opposite to the front disk 422, and blades. The blades of the present embodiment are backward blades, which are disposed between the rear disk 421 and the front disk 422 and are spaced apart from each other in the circumferential direction of the front disk 422, as shown in detail in fig. 5. The power output end of the motor 43 is drivingly connected with the rear disc 421 of the impeller 42, as shown in detail in fig. 4.
Referring to fig. 5-8, the aft-facing blade of the present embodiment includes a blade body 10, the blade body 10 having a pressure side 13 and a suction side 14. The blade body 10 is arc-shaped as a whole, and has a first side 11 and a second side 12 extending side by side in the length direction, wherein the first side 11 of the blade body 10 is an inlet edge corresponding to the inflow of the airflow, and the second side 12 is an outlet edge corresponding to the outflow of the airflow. Both lateral sides of the blade body 10 in the lateral direction are fixed to the front disk 422 and the rear disk 421, respectively.
Referring to fig. 7, the pressure side 13 of the blade body 10 is provided with a first noise reducing structure and the suction side 14 is provided with a second noise reducing structure.
The first noise reduction structure of the present embodiment includes at least one step formed by recessing from the pressure surface 13 of the blade body 10 to the suction surface 14 of the blade body 10, specifically, the step is a strip-shaped step 20 extending along the width direction of the pressure surface 13 of the blade body 10, that is, two ends of the strip-shaped step 20 extend to two side positions of the blade body 10 along the width direction of the blade body 10. Thus, the strip-shaped steps 20 divide the pressure surface 13 of the blade body 10 into at least two curved surfaces in the longitudinal direction thereof. In the present embodiment, the two strip-shaped steps 20 are preferably arranged, wherein the two strip-shaped steps 20 are sequentially arranged at intervals along the length direction of the blade body 10, so that the pressure surface 13 of the blade body 10 is divided into three arc surfaces by the two strip-shaped steps 20.
Referring to fig. 7, the three arc surfaces are a first arc surface 131, a second arc surface 132 and a third arc surface 133 from the first side 11 to the second side 12 of the blade body 10, wherein the length of the first arc surface 131 is L1, and the length of the third arc surface 133 is L3. On the other hand, the distance from the first side 11 of the blade body 10 to the center O of the impeller 42 is r1, and the distance from the second side 12 to the center O of the impeller 42 is r2, wherein the length L1 of the first arc surface satisfies the condition: l1 is less than or equal to (r2-r 1)/4; the length L3 of the third cambered surface meets the condition that: l3 is less than or equal to L1 × 3/4.
In order to stabilize and smooth the incoming flow, the strip-shaped step 20 is preferably designed to be located near the starting point of the leading edge of the blade, so as to inhibit and delay the separation of the boundary layer, and to weaken the separation vortex energy to some extent. The strip-shaped step 20 is already difficult to function if the design position of the strip-shaped step 20 is relatively far back. The other strip-shaped step 20 is designed to be close to the tail edge of the blade, so that the outlet high-pressure airflow close to the tail edge area of the blade has sufficient space for diffusion, the strength of an outlet dipole is reduced, the outlet of a flow channel is smoother, and the total pressure loss is remarkably reduced.
Referring to fig. 7, the recessed depths of the two strip steps 20 decrease in sequence from the first side edge 11 to the second side edge 12 of the blade body 10. On the other hand, the concave depth of the strip-shaped step 20 is h, and h satisfies the condition: r is1/12＜h＜r1/12+(r2-r1)/15. The purpose of the design of the structure of the pressure surface 13 in which the concave depth of the strip-shaped step 20 is gradually reduced is: because the vicinity of the front edge of the blade can be impacted by unstable airflow, namely, the pressure fluctuation of the flow field in the area of the strip-shaped step 20 close to the front edge of the blade is obvious, the strip-shaped step 20 with larger concave depth can be adopted to reduceLess pressure pulsations of unsteady incoming flow; and the strip-shaped step 20 with relatively small concave depth is adopted in the area close to the tail edge of the blade, so that the shock wave intensity of airflow at the outlet of the tail edge of the blade can be greatly reduced.
With continued reference to fig. 7, the second noise reduction structure on the suction surface 14 of the present embodiment includes at least one protrusion protruding from the suction surface 14 of the blade body 10 in a direction away from the pressure surface 13, where the protrusion is a strip-shaped protrusion 30 extending along the width direction of the suction surface 14 of the blade body 10, and the surface of each strip-shaped protrusion 30 is a cylindrical surface.
The suction surface 14 of the blade of the present embodiment has at least two strip-shaped protrusions 30, and the strip-shaped protrusions 30 are sequentially arranged at intervals along the length direction of the blade body 10, wherein the protrusion height of each strip-shaped protrusion 30 decreases sequentially from the first side 11 to the second side 12 of the blade body 10, as shown in detail in fig. 7. The above structure design can reduce the air flow speed near the wall surface of the pressure surface 13, and make the fluid flow adherent better.
With continued reference to fig. 7, the number of strip-shaped protrusions 30 on the suction side 14 of the blade of this embodiment corresponds to the number of strip-shaped steps 20 on the pressure side 13 of the backward blade. For this reason, the strip-shaped steps 20 of the present embodiment are preferably two, and the strip-shaped protrusions 30 are also two correspondingly. In the present embodiment, the vane 420 is optimally designed, and the strip-shaped protrusion 30 on the suction surface 14 of the previous blade body 10 corresponding to one vane 420 is closer to the center of the impeller 42 than the strip-shaped step 20 on the pressure surface 13 of the subsequent blade body 10.
Fig. 8 shows a pressure and streamline distribution diagram of the suction surface of the blade of the embodiment, since the horseshoe vortex position on the pressure surface 13 side of the blade does not change significantly with the increase of the fan rotation speed, and the separation vortex moves towards the direction close to the suction surface 14, so that the boundary layer on the pressure surface 13 side becomes thinner, and the boundary layer on the suction surface 14 becomes thicker, the structure of the strip-shaped protrusion 30 of the suction surface 14 of the embodiment can play a role of pulling the fluid, so that the fluid is changed into a low-speed high-pressure state after passing through the strip-shaped protrusion 30, and further the static pressure coefficient of the suction surface 14 is increased, as shown in detail by the arrow in fig. 8. The strip-shaped protrusions 30 reduce the velocity gradient in the surface area of the suction surface 14 and reduce the turbulence intensity in the cylindrical surface area, thereby reducing the shear stress of the strip-shaped protrusions 30 and achieving an effective drag reduction effect.
In the embodiment, the impeller 42 of the centrifugal fan 40 uses the structural design of the strip-shaped step 20 on the pressure surface 13 of the backward blade and the strip-shaped protrusion 30 on the suction surface 14, so that the structure of a blade path formed between two adjacent blades is optimized, the transverse swing of fluid near the suction surface 14 is effectively blocked, and the boundary layer near the suction surface 14 can be completely distributed, so that the boundary layer separation is delayed, the secondary flow generated near the suction surface 14 is inhibited, the flow state of the fluid in the blade path 420 is further improved, the fluid speed in the blade path 420 is more uniform, the secondary flow and the axial vortex in the blade path 420 are obviously reduced, and the boundary layer separation phenomenon is reduced. When fluid flows through the pressure surface 13, small vortices are generated in the structure of the strip-shaped step 20, and the vortices can enable the boundary layer which should be separated on the pressure surface 13 to adhere to the surface of the blade again, so that the shedding of the karman vortex street is inhibited, and a good rectifying effect is achieved.
Claims (9)
1. Centrifugal fan is backward blade for impeller includes:
the blade body (10) is arc-shaped as a whole and is provided with a first side edge (11) and a second side edge (12) which extend side by side in the length direction, the first side edge (11) is an inlet edge corresponding to inflow of airflow, and the second side edge (12) is an outlet edge corresponding to outflow of airflow;
it is characterized by also comprising:
the first noise reduction structure comprises at least one step formed by sinking from a pressure surface (13) of the blade body (10) to a suction surface (14) of the blade body (10), the step is a strip-shaped step (20) extending along the width direction of the pressure surface (13) of the blade body (10), and each strip-shaped step (20) divides the pressure surface (13) of the blade body (10) into at least two arc surfaces in the length direction;
the second noise reduction structure comprises at least one protrusion protruding from the suction surface (14) of the blade body (10) to the direction away from the pressure surface (13), the protrusion is a strip-shaped protrusion (30) extending along the width direction of the suction surface (14) of the blade body (10), and the surface of each strip-shaped protrusion (30) is a cylindrical surface.
2. The backward blade for the centrifugal fan impeller according to claim 1, characterized in that: the strip-shaped steps (20) are at least two and are arranged along the length direction of the blade body (10) at intervals in sequence, wherein the concave depth of each strip-shaped step (20) is reduced in sequence from the first side edge (11) to the second side edge (12) of the blade body (10).
3. The backward blade for centrifugal fan impellers of claim 2, characterized in that: the strip-shaped bulges (30) are at least two and are sequentially arranged at intervals along the length direction of the blade body (10), wherein the bulge heights of the strip-shaped bulges (30) are sequentially reduced from the first side edge (11) to the second side edge (12) of the blade body (10).
4. The backward blade for a centrifugal fan impeller according to claim 3, characterized in that: the number of the strip-shaped steps (20) is two, so that the pressure surface (13) of the blade body (10) is divided into three arc surfaces by the two strip-shaped steps (20), and the number of the strip-shaped protrusions (30) is two correspondingly.
5. The backward blade for centrifugal fan impellers of claim 4, characterized in that: the distance of first side (11) to impeller (42) center of blade body (10) is r1, and the distance of second side (12) to impeller (42) center is r2, and aforementioned three-section cambered surface certainly first side (11) to second side (12) of blade body (10) are first cambered surface (131), second cambered surface (132) and third cambered surface (133) respectively, the length of first cambered surface (131) is L1, and L1 satisfies the condition: l1 is less than or equal to (r2-r 1)/4; the length of the third cambered surface (133) is L3, and L3 meets the condition that: l3 is less than or equal to L1 × 3/4.
6. According toThe backward blade for a centrifugal fan impeller according to claim 5, characterized in that: the concave depth of the strip-shaped step (20) is h, and h meets the condition: r is1/12＜h＜r1/12+(r2-r1)/15。
7. Rearward blade for a centrifugal fan impeller according to any of claims 1 to 6, characterized in that: an impeller passage (420) is formed between two adjacent backward blades, the number of the strip-shaped protrusions (30) on the blade body (10) is correspondingly consistent with that of the strip-shaped steps (20), and the strip-shaped protrusions (30) on the suction surface (14) of the previous blade body (10) corresponding to one impeller passage (420) are closer to the center of the impeller (42) relative to the strip-shaped steps (20) on the pressure surface (13) of the next blade body (10).
8. A centrifugal fan using the backward blade as claimed in any one of claims 1 to 7, characterized in that: including volute (41), locate impeller (42) and motor (43) in volute (41), impeller (42) are including back dish (421) and front disc (422), back dish (421) with front disc (422) set up relatively, the back blade locate back dish (421) with between front disc (422), and follow the circumference interval distribution of front disc (422), the power take off of motor (43) with back dish (421) drive connection of impeller (42).
9. A range hood, its characterized in that: use is made of a centrifugal fan according to claim 8.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2021100575579 | 2021-01-15 | ||
| CN202110057557 | 2021-01-15 |
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| CN215214095U true CN215214095U (en) | 2021-12-17 |
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| CN202120748012.8U Active CN215214095U (en) | 2021-01-15 | 2021-04-13 | Backward blade for centrifugal fan impeller, centrifugal fan and range hood |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114688083A (en) * | 2022-04-28 | 2022-07-01 | 宁波方太厨具有限公司 | Blade, impeller with blade, fan system and range hood |
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2021
- 2021-04-13 CN CN202120748012.8U patent/CN215214095U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114688083A (en) * | 2022-04-28 | 2022-07-01 | 宁波方太厨具有限公司 | Blade, impeller with blade, fan system and range hood |
| CN114688083B (en) * | 2022-04-28 | 2023-02-28 | 宁波方太厨具有限公司 | Blade, impeller applying same, fan system and range hood |
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