CN111255738B - Impellers, mixed flow fans and air conditioners - Google Patents
Impellers, mixed flow fans and air conditioners Download PDFInfo
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- CN111255738B CN111255738B CN202010066092.9A CN202010066092A CN111255738B CN 111255738 B CN111255738 B CN 111255738B CN 202010066092 A CN202010066092 A CN 202010066092A CN 111255738 B CN111255738 B CN 111255738B
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- 238000004088 simulation Methods 0.000 description 5
- 238000000034 method Methods 0.000 description 3
- 239000013598 vector Substances 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 238000005457 optimization Methods 0.000 description 2
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- 230000015572 biosynthetic process Effects 0.000 description 1
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Classifications
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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
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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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- General Engineering & Computer Science (AREA)
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Abstract
The invention discloses an impeller, a mixed flow fan and an air conditioner. The impeller comprises a hub, a wheel cover and a plurality of blades, wherein the blades are connected between the outer surface of the hub and the inner surface of the wheel cover, the blades comprise front edges positioned on one side of an air inlet end, and on a transverse projection plane perpendicular to an axis, projections of contour lines of the front edges are provided with first intersection points intersecting with projections of the hub and second intersection points intersecting with projections of the wheel cover, and projections of the contour lines of the front edges are concave curves connecting the first intersection points and the second intersection points. The front edges of the blades of the impeller are approximately concave in shape, so that compared with the plane front edge, the air inlet area of the flow channel between the adjacent blades is increased under the condition that the total air inlet area of the impeller is the same, and air inlet fluency is improved.
Description
Technical Field
The invention relates to the technical field of fans, in particular to an impeller, a mixed flow fan and an air conditioner.
Background
The air path system is one of the components in the air conditioner for promoting the air in the area where the air conditioner acts to accelerate the heat exchange. In the air path system of the air conditioner, a designer selects and matches a proper fan according to the actual requirements corresponding to different models and specifications of the air conditioner so as to meet the working quality and the use comfort of the air conditioner.
In order to meet the air quantity and pressure head index of the air conditioner, a mixed flow fan is adopted in an air path system of the air conditioner in the related technology. Designers find that the blades of the mixed flow fan in the related art are planar, so that the flow passage area between adjacent blades is smaller, and the air inlet smoothness is further influenced.
Disclosure of Invention
The invention aims to provide an impeller, a mixed flow fan and an air conditioner so as to optimize the air inlet condition of the fan.
A first aspect of the present invention provides an impeller comprising:
the wheel cover comprises an inner cavity which is communicated along the axis, and the inner cavity is provided with an air inlet end and an air outlet end which are oppositely arranged;
a hub disposed in the wheel cover, and
The blades are connected between the outer surface of the hub and the inner surface of the wheel cover, the blades comprise front edges positioned on one side of the air inlet end, projection of the contour lines of the front edges on a transverse projection plane perpendicular to the axis is provided with first intersection points intersecting with projection of the hub and second intersection points intersecting with projection of the wheel cover, and projection of the contour lines of the front edges is a concave curve connecting the first intersection points and the second intersection points.
In some embodiments, the concave curve is oriented opposite the direction of rotation of the impeller.
In some embodiments, the concave curve comprises a leaf-shaped line.
In some embodiments, the angle between the tangent of the concave curve at the first intersection point and the tangent of the projection of the hub at the first intersection point ranges from [20 °,150 ° ], and/or the angle between the tangent of the concave curve at the second intersection point and the tangent of the projection of the shroud at the second intersection point ranges from [20 °,150 ° ].
In some embodiments, the angle between the tangent of the concave curve at the first intersection point and the tangent of the projection of the hub at the first intersection point is 70 DEG and/or the angle between the tangent of the concave curve at the second intersection point and the tangent of the projection of the wheel cover at the second intersection point is 78.5 deg.
In some embodiments, the line connecting the first intersection point and the second intersection point forms a chord line having a length ranging from [40mm,55mm ].
In some embodiments, the length of the string is 48mm.
In some embodiments, the line connecting the first intersection point and the second intersection point forms a chord line, and the distance between the maximum bending point of the concave curve and the chord line ranges from [2mm,12mm ].
In some embodiments, the distance between the maximum bending point of the concave curve and the chord line is 2.4mm.
In some embodiments, the line between the first intersection point and the second intersection point forms a chord line, and the projection of the maximum bending point of the concave curve on the chord line is 20% -85% of the chord length from the first intersection point.
In some embodiments, on a longitudinal projection plane passing through the axis, the projection of the contour line of the leading edge is an inclined line, and in the extending direction from the radially inner side to the radially outer side, the distance between the inclined line and the lateral reference line becomes gradually larger, and the lateral reference line is perpendicular to the axis and passes through the end point of the radially inner side of the inclined line.
In some embodiments, the maximum distance between the tilt line and the lateral reference line ranges from [0mm,15mm ].
In some embodiments, the blade includes a blade root connected to the hub and extending along an outer surface of the hub, and an outer edge opposite the blade root, a projection of a contour line of the outer edge on a longitudinal projection plane passing through the axis being a variable pitch curve, an included angle between a tangent line of the variable pitch curve and a longitudinal reference line gradually increasing in a direction from the air inlet end to the air outlet end, the longitudinal reference line being parallel to the axis.
In some embodiments, the outer edge is an S-shaped curve.
In some embodiments, the blade includes a trailing edge opposite the leading edge, the trailing edge being a concave camber line that is concave toward the outside of the blade.
In some embodiments, the number of blades is 6 to 20.
A second aspect of the invention provides a mixed flow fan comprising an impeller as provided in any one of the first aspects of the invention.
A third aspect of the present invention provides an air conditioner, including the mixed flow fan provided in the second aspect of the present invention.
According to the technical scheme provided by the invention, the impeller comprises a hub, a wheel cover and a plurality of blades, the blades are connected between the outer surface of the hub and the inner surface of the wheel cover, the blades comprise front edges positioned on one side of an air inlet end, on a transverse projection plane perpendicular to an axis, projections of contour lines of the front edges are provided with first intersection points intersecting with projections of the hub and second intersection points intersecting with projections of the wheel cover, and projections of the contour lines of the front edges are concave curves connecting the first intersection points and the second intersection points. The front edges of the blades of the impeller are approximately concave, so that compared with the plane front edge, the air inlet area of the flow channel between the adjacent blades is increased under the condition that the total air inlet area of the impeller is the same, the air inlet fluency is improved, and the air inlet resistance is correspondingly reduced due to the improvement of the air inlet fluency. When the inlet air flow direction is not concentrated, the concave surface of the front edge allows more air flows in different directions to enter the impeller so as to avoid direct impact of the air flows on the blades and reduce noise. And the concave surface of the front edge can play a role in rectifying airflows in different directions, so that the velocity distribution of the airflows is more uniform.
Other features of the present invention and its advantages will become apparent from the following detailed description of exemplary embodiments of the invention, which proceeds with reference to the accompanying drawings.
Drawings
The accompanying drawings, which are included to provide a further understanding of the application and are incorporated in and constitute a part of this specification, illustrate embodiments of the application and together with the description serve to explain the application and do not constitute a limitation on the application. In the drawings:
FIG. 1 is a schematic perspective view of an impeller according to an embodiment of the present invention;
FIG. 2 is a schematic cross-sectional view of the impeller shown in FIG. 1;
FIG. 3 is a schematic view of a partial enlarged structure of the impeller shown in FIG. 2;
FIG. 4 is a schematic view of the impeller of FIG. 1 with the shroud removed;
FIG. 5 is a schematic perspective view of one of the blades of FIG. 4;
FIG. 6 is a schematic top view of the impeller of FIG. 1;
FIG. 7 is a schematic view of a partial enlarged structure of the impeller of FIG. 6;
FIG. 8 is a schematic bottom view of the impeller of FIG. 1;
Fig. 9 to 11 are schematic views of a projection structure of another blade in fig. 4 on a longitudinal projection plane;
FIG. 12 is a velocity vector diagram of a mixed flow fan inlet flow path of the related art;
FIG. 13 is a graph of velocity vectors within an inlet flow path of a mixed flow fan in accordance with an embodiment of the present invention.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. The following description of at least one exemplary embodiment is merely exemplary in nature and is in no way intended to limit the invention, its application, or uses. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
The relative arrangement of the components and steps, numerical expressions and numerical values set forth in these embodiments do not limit the scope of the present invention unless it is specifically stated otherwise. Meanwhile, it should be understood that the sizes of the respective parts shown in the drawings are not drawn in actual scale for convenience of description. Techniques, methods, and apparatus known to one of ordinary skill in the relevant art may not be discussed in detail, but should be considered part of the authorization specification where appropriate. In all examples shown and discussed herein, any specific values should be construed as merely illustrative, and not a limitation. Thus, other examples of the exemplary embodiments may have different values. It should be noted that like reference numerals and letters refer to like items in the following figures, and thus once an item is defined in one figure, no further discussion thereof is necessary in subsequent figures.
Spatially relative terms, such as "above," "upper" and "upper surface," "above" and the like, may be used herein for ease of description to describe one device or feature's spatial relationship to another device or feature as illustrated in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as "above" or "over" other devices or structures would then be oriented "below" or "beneath" the other devices or structures. Thus, the process is carried out, the exemplary term "above" may be included. Upper and lower. Two orientations below. The device may also be positioned in other different ways and the spatially relative descriptions used herein are construed accordingly.
As shown in fig. 1, the impeller of the present embodiment includes:
the wheel cover 3 comprises an inner cavity which is communicated along the axis L, and the inner cavity is provided with an air inlet end and an air outlet end which are oppositely arranged;
a hub 1 disposed in the wheel cover 3, and
The blades 2 are connected between the outer surface of the hub 1 and the inner surface of the shroud 3, and the blades 2 include a front edge 21 located on the air inlet side, a projection of a contour line of the front edge 21 has a first intersection point E intersecting with the projection of the hub 1 and a second intersection point F intersecting with the projection of the shroud 3 on a lateral projection plane perpendicular to the axis L, and the projection of the contour line of the front edge 21 is a concave curve connecting the first intersection point E and the second intersection point F.
As shown in fig. 6 and 7, the front edge 21 of the present embodiment has a first intersection point E intersecting the hub 1 and a second intersection point F intersecting the shroud 3 in a plan view of the impeller, and the front edge 21 is a concave curve connecting the first intersection point E and the second intersection point F. That is, when the impeller is viewed from above, the front edges 21 of the blades 2 are substantially concave in shape, and when the total intake area of the impeller is the same as that of the planar front edges, the intake area of the flow paths between adjacent blades 2 increases, and the intake smoothness is improved, and the intake resistance is reduced accordingly. When the inlet air flow direction is not concentrated, the concave surface of the front edge allows more air flows in different directions to enter the impeller so as to avoid direct impact of the air flows on the blades and reduce noise. And the concave surface of the front edge can play a role in rectifying airflows in different directions, so that the velocity distribution of the airflows is more uniform.
It should be noted that, the transverse projection plane of the embodiment of the present invention is perpendicular to the axis L of the impeller. The longitudinal projection plane of the embodiment of the invention needs to pass through the axis L of the impeller. Further, the longitudinal projection surface of any one of the blades is a longitudinal projection surface facing the blade in the direction of the axis L. For example, the longitudinal projection plane of each blade 2 in fig. 4, which is located on the front side of the hub 1 and located in the middle, corresponds to the longitudinal projection plane parallel to the paper surface. That is, the position of the longitudinal projection surface differs for different blades. The longitudinal datum line of the embodiment of the invention is positioned in the longitudinal projection plane and is parallel to the axis L, and the transverse datum line is perpendicular to the axis L.
As shown in fig. 2, the internal flow channel of the mixed flow fan of this embodiment is special in form, so that the air flow flows in along the impeller axis L and then flows out obliquely. The concave design of the front edge of the vane of this embodiment is also beneficial for the air flow to flow out along such an oblique flow channel after entering the impeller.
Specifically, in the longitudinal projection plane, the impeller runner of the present embodiment is approximately a runner curve M 1M2, where an included angle α between a tangent line at the air inlet end and the longitudinal reference line of the runner curve M 1M2 ranges from [0,30 ° ], and an included angle β between a tangent line at the air outlet end and the transverse reference line ranges from [0,80 ° ].
Optionally, an included angle α between a tangent line at the air inlet end and the longitudinal reference line of the flow channel curve M 1M2 is 10 degrees, and an included angle β between a tangent line at the air outlet end and the transverse reference line is 40 degrees.
In this embodiment, the concave curve is oriented opposite to the direction of rotation of the impeller. The arrangement makes the air flow entering the impeller rotate under the wrapping of the blades 2, so that the air flow is more favorably rectified, and the speed distribution uniformity of the air flow is further improved.
Specifically, the concave curve of the present embodiment includes a leaf-shaped line. The leaf-shaped line trajectory can be obtained, for example, using the following equation.
x=p*m1*k*t/n1+t3;
y=m1*k*t2/n2+t3;
Wherein k is a parameter for adjusting the chord length of the concave curve, p= ±1 is used for adjusting the direction of the concave curve, the value range of t is m 1、n1、n2 is used for adjusting the bending degree of the concave curve.
In the present embodiment, as shown in fig. 5 and 6, the angle a between the tangent line of the concave curve at the first intersection point E and the tangent line of the projection of the hub 1 at the first intersection point E ranges from [20 °,150 ° ], preferably, the angle a is 70 °. And the angle b between the tangent of the concave curve at the second intersection point F and the tangent of the projection of the shroud 3 at the second intersection point F ranges from 20 deg., 150 deg., preferably 78.5 deg..
In this embodiment, the distance between the projection of the maximum bending point O of the concave curve on the chord line connecting the first intersection point E and the second intersection point F and the first intersection point E is 20% -85% of the chord length. The maximum bending point O here refers to the point on the concave curve where the distance from the chord line is the greatest.
The distance c between the maximum bend line O and the chord line in this embodiment ranges from 2mm to 12 mm. Preferably, the distance c between the maximum bend line O and the chord line is 2.4mm.
As shown in fig. 3, the projection of the front edge 21 on the longitudinal projection plane is an inclined line, and the vertical distance between the inclined line and the lateral reference line becomes gradually larger in the extending direction from the radially inner side to the radially outer side. The transverse reference line here refers to a transverse reference line passing through an end point of the inclined line located radially inward and perpendicular to the axis. Preferably, the maximum vertical distance h between the tilting line and the transverse reference line ranges from [0,15mm ]. More preferably, h is 6.7mm.
Fig. 9 to 11 are projections of a single blade on a longitudinal projection plane.
As shown in fig. 10, the blade 2 includes a blade root 24 connected to the outer surface of the hub 1 and extending along the outer surface of the hub 1, and a blade outer edge 22 opposite the blade root 24. The projection of the contour line of the blade outer edge 22 on the longitudinal projection plane passing through the axis L is a variable inclination curve, and the included angle between the tangent line of the variable inclination curve and the longitudinal datum line gradually increases in the direction from the air inlet end to the air outlet end.
The projection of the vane outer edge 22 on the longitudinal projection plane of the present embodiment is a variable inclination curve, and the included angle between the tangent line of the variable inclination curve and the longitudinal datum line is gradually increased, so that the vane of the present embodiment gradually guides the airflow in the flow channel, thereby avoiding a large pressure gradient and reducing flow loss.
In some embodiments, as shown in fig. 10, the variable inclination curve includes a first end point B located at the air inlet end side and a second end point C located at the air outlet end side, wherein an inlet angle d between a tangent line of the variable inclination curve at the first end point B and the longitudinal reference line ranges from [20 °,85 ° ]. The exit angle g between the tangent at the second end point C of the variable inclination curve and the longitudinal reference line ranges from [10 °,70 ° ].
Alternatively, the flow loss of the air stream was minimized when the inlet angle d was set to 50 ° and the outlet angle g was set to 57.7 ° through experimentation.
In this embodiment, as shown in fig. 10, the tilt angle curve is a first S-shaped curve. Specifically, the first S-shaped curve of the present embodiment has an inflection point and includes a first curve segment and a second curve segment located on both sides of the inflection point, respectively, and the ratio between the radius of curvature R1 of the first curve segment and the radius of curvature R2 of the second curve segment ranges from [0.2,5].
Alternatively, experiments have shown that when the radius of curvature R1 of the first curve segment is set to 125mm and the radius of curvature R2 of the second curve segment is set to 38mm, the flow loss of the air flow is minimal.
As shown in fig. 11, in the present embodiment, the projection of the blade root 24 on the longitudinal projection plane is a second S-shaped curve.
Specifically, the second S-shaped curve comprises a third end point A positioned at one side of the air inlet end and a fourth end point D positioned at one side of the air outlet end, wherein the range of an inlet included angle m between a tangent line of the second S-shaped curve at the third end point A and the transverse datum line is [65 degrees, 120 degrees ], and the range of an outlet included angle n between a tangent line of the root S-shaped line at the fourth end point D and the transverse datum line is [10 degrees, 65 degrees ]. The transverse reference line here is also not an absolute transverse reference line, but is located in a longitudinal projection plane through the axis L and perpendicular to the axis L.
Optionally, an entry angle m between a tangent line of the second S-shaped curve at the third end point a and the transverse reference line is 91 °, and an entry angle n between a tangent line of the second S-shaped curve at the fourth end point D and the transverse reference line is 24 °.
The second S-shaped curve of this embodiment has an inflection point and includes a first curve segment and a second curve segment located on both sides of the inflection point, respectively, and the ratio between the radius of curvature R 4 of the first curve segment and the radius of curvature R 3 of the second curve segment ranges from [0,3.5].
Further, the blade 2 of the present embodiment further includes a trailing edge 23 located at the air outlet end side, as shown in fig. 9, where the projection of the trailing edge 23 on the longitudinal projection plane is a concave arc. And the camber line is concave toward the outside of the blade, where the outside of the blade refers to a direction away from the blade body. That is, as shown in fig. 6, the impeller is seen from below, and the trailing edge 23 of the blade 2 is concave in general shape to avoid vortex formation during air discharge and thus optimize air flow.
In practical application, the projection length range of the tail edge chord length CD on the longitudinal projection plane is [10,30mm ], the included angle e between the tangent line at the point C of the tail edge and the chord length is [10 degrees, 50 degrees ], and the included angle f between the tangent line at the point D and the chord length is [10 degrees, 50 degrees ]. Preferably, the projection length of the chord length CD of the tail edge on the longitudinal projection plane of the embodiment is 19mm, the included angle e between the tangent line of the point C of the tail edge and the chord length is 31 °, and the included angle f between the tangent line of the point D and the chord length is 31.5 °.
The impeller of the mixed flow fan is applied to an air conditioner, and the optimal selection range of the impeller blade number is controlled to be 6-20 according to the air conditioner shell structure.
Simulation experiments are carried out on the mixed flow fan of the embodiment, and the simulation experiment is compared with the simulation of the mixed flow fan before optimization, experimental data are shown in the following table, and during the simulation experiments, noise measuring points are at the position of 0.5m of the fan outlet.
According to simulation data, under the condition that the air quantity is close, the rotating speed of the optimized fan is obviously reduced, the noise value is reduced under the same air quantity, the operation efficiency and the pressure head are improved, and the aerodynamic performance and the wind noise level of the fan are obviously improved. The comparison of the velocity vector diagrams shown in fig. 12 and 13 also shows that after optimization, the air flow entering direction along the guide ring is obviously changed, the air flow is deviated to the middle part of the flow channel, and the flow velocity distribution is more uniform and the velocity gradient is obviously slowed down through air inlet rectification.
It should be noted that the above embodiments are only for illustrating the technical solution of the present invention and not for limiting the same, and although the present invention has been described in detail with reference to the preferred embodiments, it should be understood by those skilled in the art that the specific embodiments of the present invention may be modified or some technical features may be equivalently replaced, and they are all included in the scope of the technical solution of the present invention as claimed.
Claims (16)
1. An impeller of a mixed flow fan, comprising:
The wheel cover (3) comprises an inner cavity which is communicated along the axis, and the inner cavity is provided with an air inlet end and an air outlet end which are oppositely arranged;
A hub (1) arranged in the wheel cover (3), and
A plurality of blades (2) connected between an outer surface of the hub (1) and an inner surface of the shroud (3) and the blades (2) including a front edge (21) located on the air inlet side, a projection of a contour line of the front edge (21) having a first intersection point (E) intersecting with a projection of the hub (1) and a second intersection point (F) intersecting with a projection of the shroud (3) on a lateral projection plane perpendicular to the axis, the projection of the contour line of the front edge (21) being a concave curve connecting the first intersection point (E) and the second intersection point (F);
A line connecting the first intersection point (E) and the second intersection point (F) forms a chord line, and the distance (c) between the maximum bending point (O) of the concave curve and the chord line ranges from [2mm,12mm ];
the connecting line between the first intersection point (E) and the second intersection point (F) forms a chord line, and the distance between the projection of the maximum bending point (O) of the concave curve on the chord line and the first intersection point (E) is 20% -85% of the chord length.
2. The impeller of claim 1, wherein the concave curve is oriented opposite to the direction of rotation of the impeller.
3. The impeller of claim 1, wherein the concave curve comprises a lobed line.
4. Impeller according to claim 1, characterized in that the angle (a) between the tangent of the concave curve at the first intersection point (E) and the tangent of the projection of the hub (1) at the first intersection point (E) ranges from [20 °,150 ° ], and/or the angle (b) between the tangent of the concave curve at the second intersection point (F) and the tangent of the projection of the shroud (3) at the second intersection point (F) ranges from [20 °,150 ° ].
5. Impeller according to claim 4, characterized in that the angle (a) between the tangent of the concave curve at the first intersection point (E) and the tangent of the projection of the hub (1) at the first intersection point (E) is 70 ° and/or the angle (b) between the tangent of the concave curve at the second intersection point (F) and the tangent of the projection of the shroud (3) at the second intersection point (F) is 78.5 °.
6. Impeller according to claim 1, characterized in that the line between the first intersection point (E) and the second intersection point (F) forms a chord line, the length of which ranges from [40mm,55mm ].
7. The impeller of claim 6, wherein the chord line has a length of 48mm.
8. Impeller according to claim 1, characterized in that the distance (c) between the maximum bending point (O) of the concave curve and the chord line is 2.4mm.
9. The impeller according to any one of claims 1 to 8, characterized in that the projection of the contour line of the leading edge (21) on a longitudinal projection plane through the axis is a tilting line, and in the direction of extension from the radially inner side to the radially outer side, the distance between the tilting line and a transverse reference line perpendicular to the axis and passing through the radially inner end point of the tilting line becomes progressively larger.
10. Impeller according to claim 9, characterized in that the maximum distance (h) between the tilting line and the transverse reference line ranges from [0mm,15mm ].
11. An impeller according to any one of claims 1-8, characterized in that the blade (2) comprises a blade root (24) connected to the hub (1) and extending along the outer surface of the hub (1), and an outer edge (22) opposite the blade root (24), the projection of the contour line of the outer edge (22) on a longitudinal projection plane through the axis (L) being a pitch curve, the angle between the tangent of the pitch curve and a longitudinal reference line gradually increasing in the direction from the inlet end to the outlet end, the longitudinal reference line being parallel to the axis (L).
12. Impeller according to claim 11, characterized in that the outer rim (22) is S-shaped.
13. An impeller according to any one of claims 1 to 8, characterized in that the blade (2) comprises a trailing edge (23) opposite the leading edge (21), the trailing edge (23) being a concave camber line which is concave towards the outside of the blade (2).
14. Impeller according to claim 1, characterized in that the number of blades (2) is 6 to 20.
15. A mixed flow fan comprising an impeller according to any one of claims 1 to 14.
16. An air conditioner comprising the mixed flow fan as claimed in claim 15.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010066092.9A CN111255738B (en) | 2020-01-20 | 2020-01-20 | Impellers, mixed flow fans and air conditioners |
| PCT/CN2020/138875 WO2021147604A1 (en) | 2020-01-20 | 2020-12-24 | Impeller, mixed-flow fan, and air conditioner |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202010066092.9A CN111255738B (en) | 2020-01-20 | 2020-01-20 | Impellers, mixed flow fans and air conditioners |
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| CN111255738A CN111255738A (en) | 2020-06-09 |
| CN111255738B true CN111255738B (en) | 2025-01-24 |
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| CN111255738B (en) * | 2020-01-20 | 2025-01-24 | 珠海格力电器股份有限公司 | Impellers, mixed flow fans and air conditioners |
| CN111441984B (en) * | 2020-01-20 | 2025-05-02 | 珠海格力电器股份有限公司 | Impellers, mixed flow fans and air conditioners |
| CN111156191B (en) * | 2020-01-20 | 2024-10-29 | 珠海格力电器股份有限公司 | Impeller, mixed flow fan and air conditioner |
| CN112460066B (en) * | 2020-12-21 | 2025-06-10 | 珠海格力电器股份有限公司 | Wind wheel assembly, fan assembly and fan |
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| CN211715393U (en) * | 2020-01-20 | 2020-10-20 | 珠海格力电器股份有限公司 | Impeller, mixed flow fan and air conditioner |
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