CN221120419U - Centrifugal fan blade, centrifugal fan and air conditioner - Google Patents
Centrifugal fan blade, centrifugal fan and air conditioner Download PDFInfo
- Publication number
- CN221120419U CN221120419U CN202323209780.4U CN202323209780U CN221120419U CN 221120419 U CN221120419 U CN 221120419U CN 202323209780 U CN202323209780 U CN 202323209780U CN 221120419 U CN221120419 U CN 221120419U
- Authority
- CN
- China
- Prior art keywords
- blade
- profile
- centrifugal fan
- equal
- chord length
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 230000005855 radiation Effects 0.000 description 3
- 230000003068 static effect Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
Landscapes
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The present disclosure relates to a centrifugal fan blade, a centrifugal fan and an air conditioner, wherein a blade of the centrifugal fan blade is provided with a blade middle-sized line, the blade middle-sized line is designed such that a pressure surface molded line of a pressure surface of the blade and a suction surface molded line of a suction surface of the blade are arranged at equal thicknesses on two sides of the blade middle-sized line, so that the blade thickness of the blade is equally divided, molded lines of the blade middle-sized line and the blade thickness of the blade are spline curves, and a curve control equation of the blade middle-sized line is: 10 3y＝-0.318s2x3-33.839sx2+867.23x+48.511s‑1, the curve control equation of the blade thickness is: 10 3d＝-0.083s2x3-9.214sx2+95.145x+3967.2s‑1, wherein x is more than or equal to 0 and less than or equal to b, s is more than or equal to 0.7 and less than or equal to 1.3, b is the chord length of the blade, s is a modulation correction parameter, d is the thickness of the blade, the x axis is the direction extending along the chord length of the blade, the y axis is the direction perpendicular to the chord length of the blade, and the origin of coordinates is the circle center O of an inscribed circle of the front edge of the blade.
Description
Technical Field
The utility model relates to the technical field of air conditioners, in particular to a centrifugal fan blade, a centrifugal fan and an air conditioner.
Background
With the popularization of air conditioner use, users have put higher demands on the performance of the air conditioner, especially low power and low noise. The multi-wing centrifugal fan blade is widely applied to air conditioner models such as air pipe machines, vertical cabinet machines and the like due to the advantages of compact structure, low noise, high static pressure and the like.
The design of the blade profile plays a key role in the performance of the centrifugal fan, and the fine structural characteristics of the blade based on the fluid mechanics principle can play a role in further improving the performance of the fan. In the prior art, a multi-wing centrifugal fan blade generally adopts an airfoil design, and the blade profile comprises a pressure surface, a suction surface, a leading edge and a trailing edge, and the molded lines of the blade profile are mostly circular arcs or spline lines. The centrifugal fan blade in the prior art generally takes a pressure surface and a suction surface as objects to carry out spline line design. The centrifugal fan blade in the prior art has the problems of larger resistance of a blade boundary layer, higher running power of a fan and larger noise.
The present utility model has been made in view of this.
Disclosure of utility model
In order to solve the technical problem, the performance level of the centrifugal fan is further improved, and the high-efficiency low-noise centrifugal fan blade with the molded line in the blade and the thickness of the blade as spline molded line design objects is provided. The centrifugal fan blade and the centrifugal fan system with the centrifugal fan blade remarkably reduce the running power and noise radiation level of the fan.
According to one aspect of the present utility model, there is provided a centrifugal fan blade, the centrifugal fan blade comprising a blade provided with a blade leading edge, a pressure surface, a blade trailing edge and a suction surface connected end to end in this order, characterized in that the blade is provided with a blade middle line designed such that the pressure surface line of the pressure surface of the blade and the suction surface line of the suction surface of the blade are arranged at equal thicknesses on both sides of the blade middle line so as to equally divide the blade thickness of the blade, the blade middle line and the blade thickness line of the blade are spline curves, and the curve control equation of the blade middle line is: 10 3y＝-0.318s2x3-33.839sx2+867.23x+48.511s-1, the curve control equation of the blade thickness is: 10 3d＝-0.083s2x3-9.214sx2+95.145x+3967.2s-1, wherein x is more than or equal to 0 and less than or equal to b, s is more than or equal to 0.7 and less than or equal to 1.3, b is the chord length of the blade, s is a modulation correction parameter, d is the thickness of the blade, the x axis is the direction extending along the chord length of the blade, the y axis is the direction perpendicular to the chord length of the blade, and the origin of coordinates is the circle center O of an inscribed circle of the front edge of the blade.
Further preferably, the characteristic chord length of the bladeThe characteristic chord length value of the curvature maximum value of the molded line in the blade is/>Then satisfy/>
It is further preferred that the blade is provided with a rear step, wherein the rear step is provided in the vicinity of a position where the airflow angle of the pressure surface is maximum and the boundary layer of the suction surface is most easily separated.
Further preferably, an inscribed circle with a diameter d 'is selected, the tangent points of the inscribed circle and the pressure surface and the suction surface are respectively a first tangent point P' and a second tangent point S ', the rear step comprises a suction surface step profile and a pressure surface step profile, the profile of the suction surface step profile is formed by the connection line of the second tangent point S' and the center M 'of the inscribed circle and the suction surface step profile, the profile of the pressure surface step profile is formed by the connection line of the first tangent point P' and the center M 'of the inscribed circle and the pressure surface step profile, the connection line of the second tangent point S' and the center M 'of the inscribed circle is the cutting depth hs of the suction surface step profile, and the connection line of the first tangent point P' and the center M 'of the inscribed circle is the cutting depth hp of the pressure surface step profile, wherein the characteristic chord length of the position of the center M' of the inscribed circle isThe starting point of the suction surface step profile of the rear step is defined by the characteristic chord length/>The cutting depth hs corresponding to the step profile of the suction surface is determined, and the starting point of the step profile of the pressure surface of the rear step is determined by the characteristic chord length/>And determining the cutting depth hp corresponding to the pressure surface step profile, wherein the end points of the suction surface step profile and the pressure surface step profile are tangent to the positions of the tail edges of the blades with the corresponding suction surface profile and pressure surface profile.
Further preferably, the characteristic chord lengthSatisfy/>The cutting depth hp corresponding to the pressure surface step profile is less than or equal to 0.1 and less than or equal to 0.2, and the cutting depth hs corresponding to the suction surface step profile is less than or equal to 0.1 and less than or equal to 0.2.
According to another aspect of the present utility model, there is provided a centrifugal fan comprising the centrifugal fan blade mentioned above.
According to another aspect of the present utility model, there is provided an air conditioner including the above centrifugal fan.
By adopting the technical scheme, compared with the prior art, the utility model has the following beneficial effects:
1. The high-efficiency low-noise centrifugal fan blade which takes the molded line in the blade and the thickness of the blade as spline molded line design objects is adopted, so that the running power and the noise radiation level of the fan are obviously reduced.
2. The blade is reasonably modified, the structural characteristics of the rear steps are added, and the rear steps generate stable built-in vortexes, so that the effects of reducing the surface boundary layer resistance of the blade and accelerating the surface flow are achieved, the problem of larger resistance of the blade boundary layer is solved, and the running power of the blade is reduced.
The following describes the embodiments of the present utility model in further detail with reference to the accompanying drawings.
Drawings
The accompanying drawings, which are included to provide a further understanding of the utility model and are incorporated in and constitute a part of this specification, illustrate embodiments of the utility model and together with the description serve to explain the utility model. It is evident that the drawings in the following description are only examples, from which other drawings can be obtained by a person skilled in the art without the inventive effort. In the drawings:
Fig. 1 is a schematic structural view of a basic blade profile centrifugal fan blade according to a first embodiment of the utility model.
Fig. 2 is a schematic view of a basic blade profile of the basic blade profile centrifugal fan blade shown in fig. 1.
Fig. 3 is a schematic structural view of a rear stepped vane type centrifugal fan blade according to a second embodiment of the present utility model.
Fig. 4 is a schematic view of a rear step blade profile of the rear step blade centrifugal fan blade shown in fig. 3.
Fig. 5 is a schematic view of the tangent of the trailing edge of a profile.
Fig. 6 is a graph of power of a centrifugal fan employing the basic blade-type centrifugal fan blade shown in fig. 2 and a centrifugal fan employing the rear step blade-type centrifugal fan blade shown in fig. 4 at different air volumes from a conventional centrifugal fan.
Fig. 7 is a graph of noise for a centrifugal fan using the basic blade profile centrifugal fan blade shown in fig. 2 at different air volumes from a conventional centrifugal fan.
Wherein: 1-a fan blade bottom plate, 2-a plurality of blades, 3-an impeller middle plate, 4-a rear step, 5-an inscribed circle, 6-a pressure surface tangent point, 7-a suction surface tangent point, 21-a blade front edge, 22-a pressure surface, 23-a blade tail edge and 24-a suction surface, 221-pressure side profile, 241-suction side profile, 211-blade leading edge profile 211, 231-blade trailing edge profile 231, 251-blade center profile, 2214-pressure side step profile, 2414-suction side step profile.
It should be noted that these drawings and the written description are not intended to limit the scope of the inventive concept in any way, but to illustrate the inventive concept to those skilled in the art by referring to the specific embodiments.
Detailed Description
In the description of the present utility model, it should be noted that the azimuth or positional relationship indicated by the terms "inner", "outer", etc. are based on the azimuth or positional relationship shown in the drawings, and are merely for convenience of describing the present utility model and simplifying the description, and are not indicative or implying that the apparatus or element in question must have a specific azimuth, be constructed and operated in a specific azimuth, and thus should not be construed as limiting the present utility model.
In the description of the present utility model, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "contacting," and "communicating" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium. The specific meaning of the above terms in the present utility model will be understood in specific cases by those of ordinary skill in the art.
The utility model provides a centrifugal fan blade, and fig. 1 shows a schematic structural diagram of a basic blade type centrifugal fan blade according to a first embodiment of the utility model. As shown in fig. 1, the centrifugal fan blade of this embodiment includes an integrally formed fan blade bottom plate 1, a plurality of blades 2 and an impeller middle plate 3, the fan blade bottom plate 1 is in a circular ring shape, and the plurality of blades 2 are uniformly arranged on the inner peripheral wall of the fan blade bottom plate 1 along the circumferential direction of the fan blade bottom plate 1. The basic blade profile of the blade 1 is formed by extending axially along the axis of the impeller mid-disk 3 and is evenly distributed circumferentially along the impeller mid-disk 3.
Fig. 2 shows a schematic view of a basic blade profile of the basic blade profile centrifugal fan blade shown in fig. 1. As shown in fig. 2, the blade 2 is provided with a blade leading edge 21, a pressure surface 22, a blade trailing edge 23 and a suction surface 24, which are connected in series. The pressure surface profile 221 of the pressure surface 22 and the suction surface profile 241 of the suction surface 24 are spline curves. The blade leading edge profile 211 of the blade leading edge 21 is a circular arc profile, the blade trailing edge profile 231 of the blade trailing edge 23 is a straight line profile, the blade trailing edge 23 is connected to the blade chassis 1, and the blade leading edge 21 extends toward the axis of the blade chassis 1. The profile 221 of the pressure surface 22 is the curve that the pressure surface 22 is projected along the axis of the blade floor 1, the profile 241 of the suction surface 24 is the curve that the suction surface 24 is projected along the axis of the blade floor 1, the profile 211 of the blade leading edge 21 is the curve that the blade leading edge 21 is projected along the axis of the blade floor 1, and the profile 231 of the blade trailing edge 23 is the curve that the blade trailing edge 23 is projected along the axis of the blade floor 1.
As shown in fig. 2, the blade is provided with a blade middle line 251, and the blade middle line 251 is designed to equally thickness the profile 221 of the pressure surface 22 of the blade 2 and the profile 241 of the suction surface of the blade 2 on both sides of the blade middle line 251 by controlling the variation law of the blade middle line, the inscribed circle diameter, that is, the thickness of the blade, so as to equally divide the thickness d of the blade 2. Specifically, the coordinate system XOY is established with the center point of the blade leading edge 21, that is, the center O of the inscribed circle 5 of the blade leading edge 21, with the direction along the blade chord b of the blade 2 as the X axis and with the direction perpendicular to the blade chord b as the Y axis. The points M (x, y) are any points on the middle line of the blade, and the tangent points on the corresponding pressure surface 22 and suction surface 24 are tangent points P and S respectively by adopting a free spline line design. The change rule of the molded line 251 in the blade and the thickness d of the blade all meet a cubic polynomial equation. Specifically, the curve control equation of the blade middle line 251 is: 10 3y＝-0.318s2x3-33.839sx2+867.23x+48.511s-1, the curve control equation of the blade thickness d is: 10 3d＝-0.083s2x3-9.214sx2+95.145x+3967.2s-1. Wherein x is more than or equal to 0 and less than or equal to b, s is more than or equal to 0.7 and less than or equal to 1.3, b is the chord length, and s is the modulation correction parameter.
And designing the blade 2 according to the curve equation of the blade middle molded line 251 and the curve equation of the blade thickness d, so as to obtain the high-efficiency low-noise centrifugal fan blade taking the blade middle molded line 251 and the blade thickness d as spline molded line design objects.
As a further preferred embodiment, let the characteristic chord length of the blade 2 beThe characteristic chord value at which the maximum curvature of the profile 251 in the blade is located is/>Then satisfy/>To conform to the optimized flow drag reduction design.
Fig. 3 shows a schematic structural view of a rear stepped vane type centrifugal fan blade according to a second embodiment of the present utility model. The rear sections of the pressure side 22 and suction side 24 of the blade 2 are retrofitted on the basic blade profile shown in fig. 2, adding a rear step feature. The rear step blade type centrifugal fan blade comprises a fan blade bottom plate 1, a plurality of blades 2 and an impeller middle disc 3 which are integrally formed and are shown in fig. 1, and further comprises a rear step 4, wherein the rear step 4 is arranged near the position where the airflow rotation angle of a pressure surface 22 is maximum and the boundary layer of a suction surface 24 is most easily separated, and a stable built-in rotation vortex is formed at the step position by high-speed airflow during fan operation, so that rolling friction is used for replacing sliding friction, and the effects of reducing the boundary layer resistance of the surface of the fan blade and accelerating the airflow flow of the surface are achieved, and the running power of the fan blade is reduced.
Specifically, fig. 4 shows a schematic view of a rear step blade profile of the rear step blade centrifugal fan blade shown in fig. 3. As shown in fig. 4, an inscribed circle with a certain diameter d ' is selected, the center of the inscribed circle 5 is M ', the tangent points of the inscribed circle 5 and the pressure surface 22 and the suction surface 24 are respectively a first tangent point P ' and a second tangent point S ', and the characteristic chord length of the position where the center of the inscribed circle M ' is located is the same as the characteristic chord lengthThe contour line of the rear step 4 is formed by the line between the first tangential point P ' or the second tangential point S ' and the center M ' of the inscribed circle and the pressure surface step line 2214 of the pressure surface 22 or the suction surface step line 2414 of the suction surface 24. The starting point of the pressure side step profile 2214 and suction side step profile 2414 of the aft step 4 is defined by the characteristic chord/>And the corresponding cut depths hp (cut depth of the pressure side step line 2214) and hs (cut depth of the suction side step line 2414), respectively. The end points of the pressure surface step profile 2214 and the suction surface step profile 2414 of the rear step 4 are tangential to the position of the trailing edge 23 (forming the pressure surface tangent point 6 and the suction surface tangent point 7 respectively) of the profile 221 of the pressure surface 22 of the blade 2 and the profile 241 of the suction surface of the blade 2, so as to ensure that the outlet mounting angles β1, β2 of the blade 2 are unchanged. As shown in fig. 5, taking the outlet mounting angle β1 of the pressure surface of the blade as an example, it refers to the angle between the tangential line of the pressure surface line 221 of the blade 2 at the trailing edge tangent point 6 and the circumferential rotation direction of the centrifugal fan blade. Wherein the characteristic chord length/>, of the blade 2Satisfy/>The depth of cut hp of the pressure side step profile 2214 meets 0.1.ltoreq.hp/d '. Ltoreq.0.2 and the depth of cut hs of the suction side step profile 2414 meets 0.1.ltoreq.hs/d'. Ltoreq.0.2.
The air conditioner of the utility model adopts the fan blade of the basic blade profile shown in fig. 2 and the fan blade of the rear step type blade profile shown in fig. 4, thereby remarkably reducing the running power and noise level of the fan of the air conditioner. Fig. 6 shows the wind-power curves of a wind blade using a prior art wind blade and a wind blade of a basic blade profile and a rear step blade profile according to the present utility model. Fig. 7 shows a graph of wind volume versus noise for a fan blade employing a prior art fan blade and a basic blade profile according to the present utility model. As shown in fig. 6, curve 8 represents the wind-power curve of the previous generation of blades, curve 9 represents the wind-power curve of the blades of the basic blade profile, and curve 10 represents the wind-power curve of the blades of the rear step blade profile. The power is reduced by about 12% under the static pressure outside 50Pa and the required air quantity of each rotating speed. As shown in fig. 7, a curve 11 represents the wind-noise curve of the previous generation of blades, and a curve 12 represents the wind-noise curve of the blades of the basic blade profile. As shown in FIG. 7, the noise is reduced by not less than 2dB under the conditions of the static pressure outside the machine of 50Pa and the required air quantity of each rotating speed by adopting the fan blade of the basic blade molded line shown in FIG. 2, so that the noise radiation level of the air conditioner is remarkably reduced.
The blade 2 of the utility model can be used for different types of centrifugal fan blades, can be a double-suction impeller, can also be a single-suction impeller, and can be used for centrifugal fans of different types of air conditioner types, such as air pipe machine centrifugal fans, vertical cabinet machine centrifugal fans and the like. In addition, the profile of the blade leading edge can also be an elliptic arc profile, a streamline profile, a spindle profile, a linear profile or the like. The molded lines of the tail edges of the blades can also be arc molded lines, elliptical arc molded lines and the like.
The foregoing description is only illustrative of the preferred embodiment of the present utility model, and is not to be construed as limiting the utility model, but is to be construed as limiting the utility model to any and all simple modifications, equivalent variations and adaptations of the embodiments described above, which are within the scope of the utility model, may be made by those skilled in the art without departing from the scope of the utility model.
Although the different examples have specific components shown in the drawings, embodiments of the present disclosure are not limited to these specific combinations. The components or some of the features in one example may be used in combination with the features or components in another example.
Those of ordinary skill in the art will appreciate that the above-described embodiments are exemplary and not limiting. That is, modifications of the present disclosure will fall within the scope of the claims. For that reason the following claims should be studied to determine their true scope and content.
Claims (7)
1. The utility model provides a centrifugal fan blade, centrifugal fan blade includes the blade, the blade is provided with blade leading edge, pressure side, blade trailing edge and the suction side that connect gradually from beginning to end, its characterized in that, the blade is provided with the profile in the blade, and this blade is medium-sized to be designed so that the pressure side molded lines of the pressure side of blade and the suction side molded lines of the suction side of blade are in the equal thickness arrangement in the both sides of profile in the blade to will the blade thickness halving of blade, the molded lines in the blade with the molded lines of blade thickness of blade are spline curve, the curve control equation of molded lines in the blade is: 10 3y＝-0.318s2x3-3.839sx2+867.23x+48.511s-1, the curve control equation of the blade thickness is: 10 3d＝-0.083s2x3-9.214sx2+95.145x+3967.2s-1, wherein x is more than or equal to 0 and less than or equal to b, s is more than or equal to 0.7 and less than or equal to 1.3, b is the chord length of the blade, s is a modulation correction parameter, d is the thickness of the blade, the x axis is the direction extending along the chord length of the blade, the y axis is the direction perpendicular to the chord length of the blade, and the origin of coordinates is the circle center O of an inscribed circle of the front edge of the blade.
2. The centrifugal fan blade according to claim 1, wherein the blade has a characteristic chord lengthThe characteristic chord length value of the curvature maximum value of the molded line in the blade is/>Then satisfy/>
3. A centrifugal fan blade according to claim 1 or 2, wherein the blade is provided with a rear step, wherein the rear step is arranged in the vicinity of a position where the air flow angle of the pressure surface is greatest and the boundary layer of the suction surface is most easily separated.
4. A centrifugal fan blade according to claim 3, wherein an inscribed circle with a diameter d 'is selected, the inscribed circle and the pressure surface and the suction surface are respectively a first tangent point P' and a second tangent point S ', the rear step comprises a suction surface step profile and a pressure surface step profile, the contour line of the suction surface step profile is formed by the connection of the second tangent point S' and the center M 'of the inscribed circle and a suction surface step profile, the contour line of the pressure surface step profile is formed by the connection of the first tangent point P' and the center M 'of the inscribed circle and a pressure surface step profile, the connection of the second tangent point S' and the center M 'of the inscribed circle is the cutting depth hs of the suction surface step profile, the connection of the first tangent point P' and the center M 'of the inscribed circle is the cutting depth hp of the pressure surface step profile, wherein the position of the center M' of the inscribed circle is characterized by the chord length of chordThe starting point of the suction surface step profile of the rear step is defined by the characteristic chord length/>The cutting depth hs corresponding to the step profile of the suction surface is determined, and the starting point of the step profile of the pressure surface of the rear step is determined by the characteristic chord lengthAnd determining the cutting depth hp corresponding to the pressure surface step profile, wherein the end points of the suction surface step profile and the pressure surface step profile are tangent to the positions of the tail edges of the blades with the corresponding suction surface profile and pressure surface profile.
5. Centrifugal fan blade according to claim 1 or 2, characterized by a characteristic chord lengthSatisfy/>The cutting depth hp corresponding to the pressure surface step profile is less than or equal to 0.1 and less than or equal to 0.2, and the cutting depth hs corresponding to the suction surface step profile is less than or equal to 0.1 and less than or equal to 0.2.
6. A centrifugal fan, characterized in that it comprises a centrifugal fan blade according to any one of claims 1-5.
7. An air conditioner, characterized in that it comprises a centrifugal fan according to claim 6.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202323209780.4U CN221120419U (en) | 2023-11-24 | 2023-11-24 | Centrifugal fan blade, centrifugal fan and air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202323209780.4U CN221120419U (en) | 2023-11-24 | 2023-11-24 | Centrifugal fan blade, centrifugal fan and air conditioner |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN221120419U true CN221120419U (en) | 2024-06-11 |
Family
ID=91368419
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202323209780.4U Active CN221120419U (en) | 2023-11-24 | 2023-11-24 | Centrifugal fan blade, centrifugal fan and air conditioner |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN221120419U (en) |
-
2023
- 2023-11-24 CN CN202323209780.4U patent/CN221120419U/en active Active
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US5769607A (en) | High-pumping, high-efficiency fan with forward-swept blades | |
| JP2008509323A (en) | High efficiency axial fan | |
| CN111577655B (en) | Blade and axial flow impeller using same | |
| JP2008506065A (en) | Axial fan | |
| KR20180039548A (en) | Centrifugal impeller having backward blades using dual gradient sectional shape type | |
| JPH1144432A (en) | Air conditioner | |
| JP3677214B2 (en) | Axial fan | |
| CN112253538A (en) | Axial flow wind wheel structure and axial flow fan | |
| CN110566503B (en) | Centrifugal fan blade, centrifugal fan, air conditioner and transportation means | |
| JP3077863B2 (en) | Propeller fan and air conditioner equipped with the same | |
| CN221120419U (en) | Centrifugal fan blade, centrifugal fan and air conditioner | |
| CN117366017A (en) | Centrifugal fan blade, centrifugal fan and air conditioner | |
| CN216589274U (en) | Axial flow fan blade, fan assembly, air conditioner outdoor unit and air conditioner | |
| CN110566500A (en) | Impeller of centrifugal ventilator | |
| JP4727425B2 (en) | Centrifugal impeller and clean system equipped with it | |
| CN215171030U (en) | High-load three-dimensional flow movable impeller and motor thereof | |
| CN204827981U (en) | High -efficient mixed flow fan | |
| JP2001082389A (en) | Vane design method for axial blower and axial blower | |
| CN213953981U (en) | Integrated centrifugal fan | |
| CN114483653A (en) | Volute, centrifugal fan and range hood | |
| CN211474520U (en) | Axial flow wind wheel and air conditioner | |
| CN113864231B (en) | Backward centrifugal impeller and ventilator | |
| CN114109909B (en) | Volute, centrifugal fan, range hood and volute generation method | |
| CN217873415U (en) | Blade and impeller, forward centrifugal fan and range hood with same | |
| CN216306316U (en) | Forward centrifugal fan impeller and centrifugal fan applying same |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant |