CN110657127A - Blade for centrifugal fan impeller, centrifugal fan impeller and range hood - Google Patents
Blade for centrifugal fan impeller, centrifugal fan impeller and range hood Download PDFInfo
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- CN110657127A CN110657127A CN201910872060.5A CN201910872060A CN110657127A CN 110657127 A CN110657127 A CN 110657127A CN 201910872060 A CN201910872060 A CN 201910872060A CN 110657127 A CN110657127 A CN 110657127A
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- blade
- centrifugal fan
- noise reduction
- fan impeller
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/30—Vanes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
- F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
- F04D29/283—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis rotors of the squirrel-cage type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/663—Sound attenuation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24C—DOMESTIC STOVES OR RANGES ; DETAILS OF DOMESTIC STOVES OR RANGES, OF GENERAL APPLICATION
- F24C15/00—Details
- F24C15/20—Removing cooking fumes
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention relates to a blade for a centrifugal fan impeller, the centrifugal fan impeller and a range hood, wherein the blade for the centrifugal fan impeller comprises a blade body, the blade body extends side by side along the length direction to form a first side edge and a second side edge, the first side edge is an inlet edge corresponding to the inflow of air flow, and the second side edge is an outlet edge corresponding to the outflow of air flow, and the range hood is characterized in that: only be in the export edge is equipped with the portion of making an uproar that falls that can reduce the noise, the portion of making an uproar that falls is the bar and extends along the length direction of blade body, the portion of making an uproar that falls includes two straightways and is located the curve section between two straightways, the longitudinal section of curve section along its length direction is the wave. The noise reduction part is only arranged at the outlet edge of the blade body, and compared with a structure that the noise reduction parts are arranged at the outlet edge and the inlet edge, the collision loss of airflow at the inlet of the blade is not aggravated, so that the aerodynamic noise of the impeller is not increased.
Description
Technical Field
The invention belongs to the technical field of centrifugal fans, and particularly relates to a blade for a centrifugal fan impeller, the centrifugal fan impeller and a range hood.
Background
The centrifugal fan is widely applied, the impeller is an important component of the centrifugal fan, the impeller rotates to drive gas to flow, and the structure of the impeller is set to be reasonable or not to directly influence the overall performance of the fan. When the range hood works, the motor is directly connected with the impeller to drive the impeller to rotate, and the axially sucked oil smoke is radially thrown out of the impeller from the center of the impeller under the action of centrifugal force. However, because the curvature of the blade is large, a counter pressure gradient is easily formed on the surface of the blade, flow separation at the tail edge of the suction surface is caused, the flow of a main flow area of the impeller is disturbed, and vortex shedding is generated at the tail edge, so that the flow loss is increased, meanwhile, the wall surface of the blade generates large pressure pulsation, large pneumatic noise is generated, the large pressure pulsation is a source of noise which disturbs the quiet environment, and the kitchen environment is seriously influenced.
In order to solve the problem, the centrifugal fan impeller disclosed in the chinese patent application with the patent number CN201610928410.1 (with the publication number CN106402021A) comprises a front ring and a rear ring, wherein a plurality of blades are welded and fixed between the front ring and the rear ring, the longitudinal section of each blade is in a wave shape, the transverse section of each blade is in an arc shape, the longitudinal section of each blade simulates the shell shape of a whale with a head, and the transverse section of each blade simulates the back fin shape of the whale with a head. The structure of the centrifugal fan impeller changes the position of vortex separation at the outlet of the blade, increases the distance between vortex centers, inhibits the disturbance of the vortex separation on flow, thereby reducing aerodynamic noise, and has the characteristics of bionic noise reduction, excellent aerodynamics, high efficiency and the like.
However, the impeller has disadvantages in that: 1. the air flow of the centrifugal fan is converted from the axial direction to the radial direction, a certain attack angle exists when the air flow enters the flow channel, the outlet end and the inlet section of the blade of the impeller are both designed into a wavy shape, the structure can aggravate the collision loss of the air flow at the inlet of the blade, and the aerodynamic noise of the impeller is increased; 2. along the length direction of the blade, the edge of the blade is wavy, and the part of the blade close to the front ring and the rear ring is designed into the wavy shape, so that the noise reduction effect cannot be basically exerted, and relatively dispersed outlet airflow can be caused, end face separation vortex is further easier to generate, the wall-near viscous resistance of the impeller during rotation can be increased, and the disadvantage is obviously realized.
Disclosure of Invention
The first technical problem to be solved by the present invention is to provide a blade for an impeller of a centrifugal fan, which avoids collision loss of an air flow at an inlet thereof, in view of the current state of the prior art.
The second technical problem to be solved by the present invention is to provide a blade for an impeller of a centrifugal fan, which can reduce the viscous resistance when the impeller rotates, in view of the current state of the prior art.
The third technical problem to be solved by the present invention is to provide a centrifugal fan impeller using the above-mentioned blades, which can avoid the collision loss of the air flow at the blade inlet and reduce the viscous resistance of the impeller when rotating, in view of the current situation of the prior art.
The fourth technical problem to be solved by the invention is to provide a range hood applying the centrifugal fan impeller, which can avoid collision loss of airflow at the inlet of the blade and reduce viscous resistance of the impeller during rotation, aiming at the current situation of the prior art.
In order to solve the first and second technical problems, the invention adopts the technical scheme that: the utility model provides a blade for centrifugal fan impeller, includes the blade body, the blade body has first side and second side along length direction side by side extension, and wherein the entry edge that first side is for corresponding the air current inflow, and the second side is for corresponding the export edge that the air current flows out, its characterized in that: only be in the export edge is equipped with the portion of making an uproar that falls that can reduce the noise, the portion of making an uproar that falls is the bar and extends along the length direction of blade body, the portion of making an uproar that falls includes two straightways and is located the curve section between two straightways, the longitudinal section of curve section along its length direction is the wave.
In order to fully exert the function of the curve segment of the noise reduction part and consider the gas fluidity inside the multi-wing centrifugal fan, the linear distance between the two end parts of the noise reduction part is H, the lengths of the two linear segments are H1 and H2 respectively, and the three meet the conditions: h2 is more than or equal to 0 and less than or equal to H1 is more than or equal to 0.1H.
In order to further reduce noise, the cross section of the blade in the width direction is arc-shaped, the total arc length of the blade body and the noise reduction part is L, the arc length of the noise reduction part is L1, and L1 is more than or equal to 0.08L and less than or equal to 0.5L. The multi-wing centrifugal fan airflow is in a process of changing from axial to radial, when L1 is too large, because of the fact that a sufficient front end buffer area is not available, a large attack angle still exists when the airflow enters from the inlet edge of the blade and then turns into the noise reduction part, the airflow can impact the wall surface of a 'wave' flow channel of the noise reduction part more, the through-flow loss of the flow channel of the blade can be increased, and the noise is increased; when the L1 is too small, the movement state of the airflow basically needs to be changed suddenly when the airflow passes through the noise reduction part, and the airflow approaches to complete the speed-increasing and pressure-increasing process (the rotating blades do work to increase the speed and pressure of the airflow) when entering the noise reduction part, so that the movement state of the airflow is difficult to change again, the noise reduction part only enables the airflow to generate severe collision loss at the outlet edge of the blades, and the airflow enters the volute flow channel in a very turbulent state, so that the noise is increased.
In order to further reduce noise, the curve section of the noise reduction part comprises concave parts and convex parts which are alternately arranged and connected, namely the curve section is designed into a continuous wave shape with wave crests and wave troughs, wherein the wave crest value and the wave trough value are A, the linear distance between the starting end of the concave part and the tail end of the convex part adjacent to the concave part is B along the length direction of the curve section, the radiuses of the concave part and the convex part are R, and the three meet the conditions: a is less than or equal to B/4 is less than or equal to R.
Preferably, a straight-line distance B between a start end of the concave portion and a tip end of the convex portion adjacent thereto is in a range of 4A ≦ B ≦ min [ R, (H-H1-H2)/5], and (H-H1-H2)/(B/2) ═ N, N is a natural number greater than 0. The value of B is controlled within a proper range, if the value is too large, the wave-shaped effect cannot be achieved, and if the value is too small, abnormal sound caused by the outlet turbulent flow wedge can be formed.
In order to avoid the over-dispersion of the airflow at the blade outlet, the peak value and the trough value should not be too large, and preferably, the range of the peak value and the trough value of the curve segment of the noise reduction part is 0.5mm or more and A or less and 5mm or less.
In order to facilitate processing and manufacturing and ensure the firmness of the blade, the blade body and the noise reduction part are integrally formed.
In order to solve the third technical problem, the technical scheme adopted by the invention is as follows: a centrifugal fan impeller applying the blades.
The impeller can be in various structural forms, and preferably, the impeller comprises
A front ring;
a rear ring disposed opposite to the front ring;
the wheel disc is positioned between the front ring and the rear ring, the edge of the wheel disc is connected with the rear ring through at least two strip-shaped spokes, and a through hole allowing the output shaft of the motor to pass through and be fixed is formed in the wheel disc;
the blades are arranged at intervals along the circumferential direction of the front ring, two ends of each blade are fixed on the front ring and the rear ring respectively, the inlet edge of each blade is close to the axis of the front ring, and the outlet edge of each blade is far away from the axis of the front ring.
Preferably, the noise reduction portion has a straight line segment with a length H1 disposed near the front ring and a straight line segment with a length H2 disposed near the rear ring, so that the curved line segment does not cause viscous drag and can fully exert its effect.
In order to solve the fourth technical problem, the technical scheme adopted by the invention is as follows: a range hood applying the centrifugal fan impeller.
Compared with the prior art, the invention has the advantages that: 1. the noise reduction part is arranged, so that the vortex separation position at the outlet of the blade is changed, the distance between vortex centers is increased, the disturbance of the vortex separation on the flow is inhibited, and the impact of airflow at the outlet of the blade on the annular wall of the volute is dispersed, so that the purpose of reducing noise is achieved, the acting capacity of the impeller is not weakened, the collision loss of the airflow at the inlet of the blade is not aggravated, and the noise reduction effect can be achieved for different flow conditions; 2. the noise reduction part is only arranged at the outlet edge of the blade body, and compared with a structure that the noise reduction part is arranged at the outlet edge and the inlet edge, the collision loss of the airflow at the inlet of the blade is not aggravated, so that the aerodynamic noise of the impeller is not increased; 3. the noise reduction part comprises a curved section and two straight sections, wherein the two straight sections are respectively positioned at two end parts of the noise reduction part in the length direction, otherwise, the end parts of the noise reduction part are also wavy, the wavy end parts cannot play a noise reduction role, relatively dispersed outlet airflow is caused, end surface separation vortex is generated, and the near wall viscous resistance of the impeller during rotation is increased, which is obviously unfavorable, and the structure of the noise reduction part avoids the problem.
Drawings
FIG. 1 is a schematic structural view of a blade according to an embodiment of the present invention;
FIG. 2 is a schematic view of the structure of FIG. 1 in another direction;
FIG. 3 is a schematic structural diagram of the noise reducing part in FIG. 1;
fig. 4 is a centrifugal fan impeller employing the blades of fig. 1.
Detailed Description
The invention is described in further detail below with reference to the accompanying examples.
As shown in fig. 1 to 4, the range hood of the preferred embodiment includes a housing and a centrifugal fan disposed in the housing, the centrifugal fan includes a motor and a centrifugal fan impeller connected to an output shaft of the motor, and in this embodiment, the centrifugal fan impeller includes a front ring 3, a rear ring 4 disposed opposite to the front ring 3, a wheel disc 5, and at least two blades a.
As shown in fig. 4, the wheel disc 5 is located between the front ring 3 and the rear ring 4, the rim of the wheel disc 5 is connected to the rear ring 4 by at least two strip webs 51, and the wheel disc 5 is provided with a through hole 52 for allowing the output shaft of the motor to pass through and be fixed.
A plurality of blades A are arranged along the circumferential direction of the front ring 3 at intervals, and two ends of each blade A are respectively fixed on the front ring 3 and the rear ring 4.
Of course, the blade a of the present embodiment is not limited to be used in the impeller of the above-mentioned structural form, and may also be used in centrifugal fan impellers of other structural forms, such as the impeller structure disclosed in CN 201610297293.3.
As shown in fig. 1 and 2, each blade a includes a blade body 1, the blade body 1 extends side by side along a length direction to have a first side and a second side, where the first side is an inlet edge 1a corresponding to an inflow of an airflow, the second side is an outlet edge 1b corresponding to an outflow of the airflow, the inlet edge 1a of each blade a is close to an axis of the front ring 3, and the outlet edge 1b is far from the axis of the front ring 3.
A noise reduction portion 2 capable of reducing noise is formed only at the outlet edge 1b of the blade body 1, and the noise reduction portion 2 is strip-shaped and extends in the longitudinal direction of the blade body 1.
As shown in fig. 1 to 3, the noise reduction part 2 includes two straight line segments and a curved line segment 22 located between the two straight line segments, and the longitudinal section of the curved line segment 22 along the length direction thereof is wavy. In order to fully exert the function of the curved section 22 of the noise reduction part 2 and consider the gas fluidity inside the sirocco fan, as shown in fig. 3, the linear distance between the two end portions of the noise reduction part 2 is H, the lengths of the two linear sections are H1 and H2, respectively, and the three satisfy the condition: h2 is more than or equal to 0 and less than or equal to H1 is more than or equal to 0.1H. Namely, a straight line segment 21a having a length H1, a curved line segment 22, and a straight line segment 21b having a length H2 are provided along the longitudinal direction of the noise damper 2. In this embodiment, the straight line segment 21a of the noise reduction unit 2 having the length H1 is disposed near the front ring 3, and the straight line segment 21b of the noise reduction unit 2 having the length H2 is disposed near the rear ring 4, so that the curved line segment 22 does not cause viscous resistance, but can sufficiently exert its effect.
As shown in fig. 3, the cross section of the blade along the width direction is arc-shaped, that is, the cross section of the blade body 1 in the width direction is arc-shaped, the cross section of the noise reduction part 2 in the width direction is arc-shaped, the total arc length of the blade body 1 and the noise reduction part 2 is L, the arc length of the noise reduction part 2 is L1, and the two satisfy the condition: l1 is more than or equal to 0.08L and less than or equal to 0.5L. The multi-wing centrifugal fan airflow is in a process of changing from axial to radial, when L1 is too large, because of the lack of a sufficient front end buffer area, the airflow enters from the inlet edge 1a of the blade A and then turns into the noise reduction part 2, a larger attack angle still exists, so that the airflow can impact the wall surface of a wave flow channel of the noise reduction part 2 more, the through-flow loss of the blade flow channel can be increased, and the noise is increased; when L1 is too small, the movement state of the airflow basically needs to change suddenly when the airflow passes through the noise reduction part 2, and the airflow approaches to complete the speed-increasing and pressure-increasing process (the blades rotate to do work to increase the speed and pressure of the airflow) when entering the noise reduction part 2, at this time, it is difficult to change the movement state of the airflow again, and the noise reduction part 2 only causes the airflow to generate severe collision loss at the outlet edge 1b of the blades, and causes the airflow to enter the volute flow channel in a very turbulent state, so that the noise is increased.
As shown in fig. 1 and 3, the curved section 22 of the noise reduction part 2 includes concave parts 221 and convex parts 222 alternately arranged and connected, the concave parts 221 and the adjacent convex parts 222 are in tangential engagement, that is, the curved section 22 is designed into a continuous wave shape with peaks and valleys, wherein the peak value and the valley value are both a, along the length direction of the curved section 22, the linear distance between the starting end of the concave part 221 and the end of the convex part 222 adjacent to the starting end is B, and the radii of the concave part 221 and the convex part 222 are both R, which satisfy the following conditions: B/4R, 4A B min [ R, (H-H1-H2)/5], and (H-H1-H2)/(B/2) N, N being a natural number greater than 0. The value of B is controlled within a proper range, if the value is too large, the wave-shaped effect cannot be achieved, and if the value is too small, abnormal sound caused by the outlet turbulent flow wedge can be formed.
In addition, in order to avoid the air flow at the outlet of the blade A from being too dispersed, the peak value and the trough value should not be too large, and the range of the peak value and the trough value of the curve segment 22 of the noise reduction part 2 is preferably more than or equal to 0.5mm and less than or equal to A and less than or equal to 5 mm.
Specifically, in this embodiment, L22 mm, L1 mm, H115 mm, H1 mm 2.5mm, H2 mm 2.5mm, a 0.5mm, B20 mm, R25.25 mm, (H-H1-H2)/(B/2) (115-2.5-2.5)/(20/2): 11 is a natural number, and compared with the conventional blade, the noise of the centrifugal blower with multiple blades in this embodiment is reduced by 0.2dB to 0.6dB for the same flow rate under different drag conditions, and the aerodynamic performance of the blower is not deteriorated.
Claims (10)
1. The utility model provides a blade for centrifugal fan impeller, includes blade body (1), blade body (1) extends side by side along length direction has first side and second side, and wherein first side is for corresponding the entry edge (1a) that the air current flows in, and the second side is for corresponding the exit edge (1b) that the air current flows out, its characterized in that: only be equipped with noise reduction portion (2) that can reduce noise in export edge (1b) department, noise reduction portion (2) are the bar and extend along the length direction of blade body (1), noise reduction portion (2) include two straightway (21a,21b) and be located two straightway (21a,21b) between curve section (22) on length direction, curve section (22) are the wave along its length direction's longitudinal section.
2. The blade for a centrifugal fan impeller according to claim 1, wherein: the straight-line distance between two end parts of the noise reduction part (2) is H, the lengths of the two straight-line segments (21a,21b) are H1 and H2 respectively, and the three satisfy the conditions that: h2 is more than or equal to 0 and less than or equal to H1 is more than or equal to 0.1H.
3. The blade for a centrifugal fan impeller according to claim 1, wherein: the blade is arc-shaped along the cross section of the width direction of the blade, the total arc length of the blade body (1) and the noise reduction part (2) is L, the arc length of the noise reduction part (2) is L1, and the two meet the conditions: l1 is more than or equal to 0.08L and less than or equal to 0.5L.
4. The blade for a centrifugal fan impeller according to claim 1, wherein: the curve section (22) of the noise reduction part (2) comprises concave parts (221) and convex parts (222) which are alternately arranged and connected, namely the curve section (22) is designed into a continuous wave shape with wave crests and wave troughs, wherein the wave crest value and the wave trough value are A, the linear distance between the starting end of the concave part (221) and the tail end of the convex part (222) adjacent to the concave part is B along the length direction of the curve section (22), the radiuses of the concave part (221) and the convex part (222) are R, and the three meet the condition that: a is less than or equal to B/4 is less than or equal to R.
5. The blade for a centrifugal fan impeller according to claim 4, wherein: the linear distance B between the start end of the concave portion (221) and the end of the convex portion (222) adjacent thereto is in the range of 4 A.ltoreq.B.ltoreq.min [ R, (H-H1-H2)/5], and (H-H1-H2)/(B/2) ═ N, N being a natural number greater than 0.
6. The blade for a centrifugal fan impeller according to claim 4, wherein: the range of the wave peak value and the wave valley value of the curve section (22) of the noise reduction part (2) is more than or equal to 0.5mm and less than or equal to A and less than or equal to 5 mm.
7. A centrifugal fan impeller using the blade of any one of claims 1 to 6.
8. The impeller for centrifugal fans of claim 7, wherein: the impeller comprises
A front ring (3);
a rear ring (4) arranged opposite to the front ring (3);
the wheel disc (5) is positioned between the front ring (3) and the rear ring (4), the edge of the wheel disc (5) is connected with the rear ring (4) through at least two strip-shaped webs (51), and a through hole (52) allowing the output shaft of the motor to penetrate through and be fixed is formed in the wheel disc (5);
the blades (A) are arranged at intervals along the circumferential direction of the front ring (3), two ends of each blade (A) are respectively fixed on the front ring (3) and the rear ring (4), the inlet edge (1a) of each blade (A) is close to the axis of the front ring (3), and the outlet edge (1b) is far away from the axis of the front ring (3).
9. The centrifugal fan impeller of claim 8, wherein: the straight line segment (21a) of the noise reduction part (2) with the length of H1 is arranged close to the front ring (3), and the straight line segment (21b) with the length of H2 is arranged close to the rear ring (4).
10. A range hood using the centrifugal fan impeller as claimed in any one of claims 7 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910872060.5A CN110657127B (en) | 2019-09-16 | 2019-09-16 | Blade for centrifugal fan impeller, centrifugal fan impeller and range hood |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201910872060.5A CN110657127B (en) | 2019-09-16 | 2019-09-16 | Blade for centrifugal fan impeller, centrifugal fan impeller and range hood |
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| CN110657127A true CN110657127A (en) | 2020-01-07 |
| CN110657127B CN110657127B (en) | 2021-11-19 |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114109924A (en) * | 2020-08-28 | 2022-03-01 | 宁波方太厨具有限公司 | Impeller, fan system applying same and range hood |
| CN114474558A (en) * | 2021-12-31 | 2022-05-13 | 太仓市福鑫防腐设备有限公司 | Centrifugal ventilator impeller and integrated injection molding manufacturing method thereof |
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| CN1914424A (en) * | 2004-09-30 | 2007-02-14 | 大金工业株式会社 | Impeller for blower and air conditioner having the same |
| CN103696985A (en) * | 2013-11-30 | 2014-04-02 | 宁波方太厨具有限公司 | Centrifugal fan impeller |
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| CN208203655U (en) * | 2018-01-15 | 2018-12-07 | 武汉朗迪叶轮机械有限公司 | Through-flow fan blade |
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| CN109667790A (en) * | 2019-01-24 | 2019-04-23 | 大连海事大学 | A kind of bionical leading edge blade of INVESTIGATION ON A HIGH SPEED CENTRIFUGAL COMPRESSOR |
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| CN114109924A (en) * | 2020-08-28 | 2022-03-01 | 宁波方太厨具有限公司 | Impeller, fan system applying same and range hood |
| CN114109924B (en) * | 2020-08-28 | 2023-04-14 | 宁波方太厨具有限公司 | Impeller, fan system applying same and range hood |
| CN114474558A (en) * | 2021-12-31 | 2022-05-13 | 太仓市福鑫防腐设备有限公司 | Centrifugal ventilator impeller and integrated injection molding manufacturing method thereof |
| CN114474558B (en) * | 2021-12-31 | 2024-04-26 | 太仓市福鑫防腐设备有限公司 | Centrifugal ventilator impeller and integral injection molding manufacturing method thereof |
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