CN111156191B - Impeller, mixed flow fan and air conditioner - Google Patents
Impeller, mixed flow fan and air conditioner Download PDFInfo
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- CN111156191B CN111156191B CN202010063828.7A CN202010063828A CN111156191B CN 111156191 B CN111156191 B CN 111156191B CN 202010063828 A CN202010063828 A CN 202010063828A CN 111156191 B CN111156191 B CN 111156191B
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- 238000004088 simulation Methods 0.000 description 5
- 238000005457 optimization Methods 0.000 description 3
- 239000013598 vector Substances 0.000 description 3
- 238000005452 bending Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000002474 experimental method Methods 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
- F04D29/666—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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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention discloses an impeller, a mixed flow fan and an air conditioner. The impeller comprises an impeller cover, a hub and a plurality of blades, wherein the impeller cover comprises an inner cavity which is communicated along an axis, and the inner cavity is provided with an air inlet end and an air outlet end which are oppositely arranged; the hub is arranged in the wheel cover; the blades are connected between the inner surface of the wheel cover and the outer surface of the wheel hub, the blades comprise blade roots connected with the outer surface of the wheel hub and extending along the outer surface of the wheel hub, and blade outer edges opposite to the blade roots, the projection of the profile line of the blade outer edges on a longitudinal projection plane passing through the axis is a variable inclination angle curve, and the included angle between the tangent line of the variable inclination angle curve and a longitudinal datum line is gradually increased in the direction from the air inlet end to the air outlet end. The projection of the outer edge of the blade on the longitudinal projection plane is a variable inclination angle curve, and the included angle between the tangent line of the variable inclination angle curve and the longitudinal datum line is gradually increased, so that the blade gradually guides the airflow in the flow channel, thereby avoiding large pressure gradient and reducing flow loss.
Description
Technical Field
The invention relates to the technical field of electric appliances, 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 have found that the pressure gradient of the air flow in the flow passage of the mixed flow fan in the related art is large, thereby causing great flow loss.
Disclosure of Invention
The invention provides an impeller, a mixed flow fan and an air conditioner, which are used for avoiding flow loss caused by large pressure gradient.
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;
The hub is arranged in the wheel cover; and
The blades are connected between the inner surface of the wheel cover and the outer surface of the wheel hub, each blade comprises a blade root connected with the outer surface of the wheel hub and extending along the outer surface of the wheel hub and a blade outer edge opposite to the blade root, the projection of the profile line of the blade outer edge on a longitudinal projection plane passing through the axis is a variable inclination angle curve, the included angle between a tangent line of the variable inclination angle curve and a longitudinal datum line is gradually increased in the direction from the air inlet end to the air outlet end, and the longitudinal datum line is parallel to the axis.
In some embodiments, the variable-inclination curve comprises a first end point positioned at the air inlet end side and a second end point positioned at the air outlet end side, wherein the range of an inlet included angle between a tangent line of the variable-inclination curve at the first end point and the longitudinal datum line is [20 °,85 ° ]; and/or the exit angle between the tangent line of the variable inclination curve at the second end point and the longitudinal reference line ranges from [10 °,70 ° ].
In some embodiments, the inlet angle is 50 ° and the outlet angle is 57.7 °.
In some embodiments, the pitch curve is a first S-shaped curve.
In some embodiments, the first S-shaped curve has an inflection point and includes a first curve segment and a second curve segment on opposite sides of the inflection point, respectively, the ratio between the radius of curvature of the first curve segment and the radius of curvature of the second curve segment ranging from [0.2,5].
In some embodiments, the radius of curvature of the first curve segment is 125mm and the radius of curvature of the second curve segment is 38mm.
In some embodiments, the projection of the blade root on the longitudinal projection plane is a second S-shaped curve.
In some embodiments, the second S-shaped curve includes a third end point located on the air inlet end side and a fourth end point located on the air outlet end side, wherein an inlet included angle between a tangent line of the second S-shaped curve at the third end point and the transverse reference line ranges from [65 °,120 ° ]; and/or the outlet angle between the tangent of the second S-shaped curve at the fourth end point and the transverse reference line ranges from [10 °,65 ° ].
In some embodiments, the entry angle between the tangent to the second S-shaped curve at the third end point and the transverse reference line is 91 ° and the entry angle between the tangent to the second S-shaped curve at the fourth end point and the transverse reference line is 24 °.
In some embodiments, the blade further comprises a leading edge on the air inlet side, the profile of the leading edge being projected as a concave curve on a transverse projection plane perpendicular to the axis.
In some embodiments, the blade is a twisted blade, and the surface of the twisted blade includes a first curved surface section, a second curved surface section, and a third curved surface section that are sequentially arranged from the air inlet end to the air outlet end, where the second curved surface section is located between the first curved surface section and the third curved surface section and is recessed toward a rotation direction side of the impeller relative to the first curved surface section and the third curved surface section.
In some embodiments, the first curved surface section, the second curved surface section and the third curved surface section are transitioned by an arc surface.
In some embodiments, the blade further comprises a trailing edge located on the side of the air outlet end, and the projection of the contour line of the trailing edge on the longitudinal projection plane is a concave arc.
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 according to any of the first aspects of the invention.
A third aspect of the present invention provides an air conditioner comprising a mixed flow fan as in the second aspect of the present invention.
Based on the technical scheme provided by the invention, the impeller comprises a wheel cover, a wheel hub and a plurality of blades, wherein the wheel cover comprises an inner cavity which is communicated along an axis, and the inner cavity is provided with an air inlet end and an air outlet end which are oppositely arranged; the hub is arranged in the wheel cover; the blades are connected between the inner surface of the wheel cover and the outer surface of the wheel hub, the blades comprise blade roots connected with the outer surface of the wheel hub and extending along the outer surface of the wheel hub, and blade outer edges opposite to the blade roots, the projection of the profile line of the blade outer edges on a longitudinal projection plane passing through the axis is a variable inclination angle curve, the included angle between a tangent line of the variable inclination angle curve and a longitudinal datum line is gradually increased in the direction from the air inlet end to the air outlet end, and the longitudinal datum line is parallel to the axis. The projection of the outer edge of the blade on the longitudinal projection plane is a variable inclination angle curve, and the included angle between the tangent line of the variable inclination angle curve and the longitudinal datum line is gradually increased, so that the blade gradually guides the airflow in the flow channel, thereby avoiding large pressure gradient and reducing flow loss.
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 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 denote 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 … …," "above … …," "upper surface on … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial location relative 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 exemplary term "above … …" may include both orientations "above … …" and "below … …". The device may also be positioned in other different ways (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.
The specific structure of the impeller according to the embodiment of the present invention will be described in detail with reference to fig. 1 to 13.
As shown in fig. 1,2, 5 and 10, the impeller of the embodiment of the invention comprises a hub 1, a shroud 3 and a plurality of blades 2, wherein the shroud 3 comprises an inner cavity penetrating along an axis, and the inner cavity is provided with an air inlet end and an air outlet end which are oppositely arranged; the hub 1 is arranged in the wheel cover 3; a plurality of blades 2 are connected between the inner surface of the shroud 3 and the outer surface of the hub 1, and the blades 2 include a blade root portion 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 portion 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 is a variable inclination angle curve, and the included angle between the tangent line of the variable inclination angle curve and the longitudinal datum line is gradually increased, so that the vane of the embodiment gradually guides the airflow in the flow channel, thereby avoiding large pressure gradient and reducing flow loss.
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.
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 a transverse datum line is [65 degrees, 120 degrees ]; the outlet angle n between the tangent of the second S-shaped curve at the fourth end point D and the transverse reference line ranges from [10 °,65 ° ]. 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].
As shown in fig. 4, the blade 2 further comprises a front edge 21 at the side of the air inlet end. As shown in fig. 7, the projection of the contour line of the leading edge 21 on the lateral projection plane perpendicular to the axis L is a concave curve. That is, the impeller is viewed from above, and the front edges 21 of the blades 2 thereof are substantially concave in shape, thereby serving to alleviate air intake resistance and direct impact on the blades to improve air intake smoothness so that the fan operates with high efficiency and low noise.
In this embodiment, the blade 2 is a twisted blade. The twisted blade comprises three curved surface sections from an air inlet end to an air outlet end, wherein the three curved surface sections are a first curved surface section, a second curved surface section and a third curved surface section respectively, and the second curved surface section is positioned between the first curved surface section and the third curved surface section and is recessed towards one side of the rotation direction of the impeller relative to the first curved surface section and the third curved surface section. That is to say, the twisted blades of the embodiment are of double twisted structure, so that the arrangement can reduce the airflow and flow separation in the inner flow channel, avoid the generation of a large amount of vortex and optimize the airflow and flow condition of the whole fan.
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 concave camber line is concave towards the outside of the blade, which here refers to the side remote from the blade body. 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 to optimize air flow.
When the impeller of the present embodiment is applied to a mixed flow fan and the mixed flow fan is applied to an air conditioner, the number of blades is set to 6 to 20.
The structure of the impeller according to the embodiment of the present invention will be described in detail with reference to fig. 1 to 11.
As shown in fig. 1, the impeller of the present embodiment includes a hub 1, a shroud 3, and a plurality of blades 2; wherein. The wheel cover 3 is provided with 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 respectively positioned at two ends. Wherein, the air inlet end is located the upside, and the air outlet end is located the downside. As shown in fig. 2, the outer surface of the hub 1 is generally conical. The wheel cover 3 is coaxially sleeved on the outer side of the wheel hub 1. A plurality of blades 2 are connected between an outer surface of the hub 1 and an inner surface of the shroud 3. As shown in fig. 4, each blade 2 includes a leading edge 21 on the air inlet side, a trailing edge 23 on the air outlet side, a blade root 23 connected to the outer surface of the hub 1 and extending along the outer surface of the hub 1, and an outer edge 22 opposite to the blade root 23.
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, the projection of the contour line of the leading edge 21 in the lateral projection plane perpendicular to the axis L is a concave curve. The projection of the blades 21 of the impeller in the transverse projection plane is a concave curve so as to slow down the air inlet resistance and the direct impact of the air flow on the blades, thereby optimizing the air inlet condition and being beneficial to the efficient low-noise operation of the fan. In this embodiment, the concave curve is oriented opposite to the direction of rotation of the impeller. Specifically, as shown in fig. 7, the impeller of the present embodiment rotates counterclockwise. This arrangement can further improve the air intake smoothness.
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 to adjust the orientation of the concave curve; the value range of t is; m 1、n1、n2 is used to adjust the degree of curvature of the concave curve.
In the present embodiment, as shown in fig. 6 and 7, the angle a between the tangent of the concave curve at the first intersection point E and the tangent of the contour line of the hub 1 at the first intersection point E ranges from [20 °,150 ° ], preferably from 70 °. And the angle b between the tangent of the concave curve at the second intersection point F and the tangent of the shroud 3 at the second intersection point F is in the range of 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 a 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.
In some embodiments, the number of blades is 6 to 20.
Fig. 9 to 11 show the projection of a single blade onto a longitudinal projection plane.
In this embodiment, as shown in fig. 8 and 9, the trailing edge of the trailing edge 23 is projected as a concave arc. The design of the tail edge of the concave arc line can optimize the flow condition of the mixed flow fan to the greatest extent, reduce the flow separation of the air flow in the flow channel inside the mixed flow fan and avoid the generation of a large amount of vortex shedding.
In practical application, the two end points of the concave arc line are a second end point C and a fourth end point D respectively, the length range of the chord line CD is [10mm,30mm ], the included angle e between the tangent line of the concave arc line at the second end point C and the chord line is [10 degrees, 50 degrees ], and the included angle f between the tangent line of the concave arc line at the fourth end point D and the chord line is [10 degrees, 50 degrees ]. Preferably, the chord line CD of this embodiment has a length of 19mm, the angle e between the tangent to the concave arc at the second end point C and the chord line is 31 °, and the angle f between the tangent to the concave arc at the fourth end point D and the chord line is 31.5 °.
As shown in fig. 10, the projection of the outer edge 22 of the blade 2 of the present embodiment on the longitudinal projection plane is a pitch arc, and the pitch angle between the tangent line of the pitch arc and the longitudinal reference line gradually increases in the direction from the air inlet end to the air outlet end.
Specifically, as shown in fig. 10, the outer edge 22 of the present embodiment is an S-shaped curve.
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.
Through the above optimization design, as shown in fig. 2, the internal flow channel of the mixed flow fan of the embodiment has a special form, so that the air flow flows in along the impeller axis L and then flows out obliquely. 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.
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.
Finally, 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; while the invention has been described in detail with reference to the preferred embodiments, those skilled in the art will appreciate that: modifications may be made to the specific embodiments of the present invention or equivalents may be substituted for part of the technical features thereof; without departing from the spirit of the invention, it is intended to cover the scope of the invention as claimed.
Claims (14)
1. An impeller, 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 the inner surface of the shroud (3) and the outer surface of the hub (1), wherein the blades (2) comprise blade roots (24) connected with the outer surface of the hub (1) and extending along the outer surface of the hub (1), and blade outer edges (22) opposite to the blade roots (24), the projection of the contour line of the blade outer edges (22) on a 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, and the longitudinal datum line is parallel to the axis (L);
The variable dip curve is a first S-shaped curve having an inflection point and including a first curve segment and a second curve segment located on either side of the inflection point, respectively, the ratio between the radius of curvature (R 1) of the first curve segment and the radius of curvature (R 2) of the second curve segment ranging from [0.2,5].
2. Impeller according to claim 1, characterized in that the variable-pitch curve comprises a first end point (B) at the air inlet end side and a second end point (C) at the air outlet end side, wherein the inlet angle (d) between the tangent of the variable-pitch curve at the first end point (B) and the longitudinal reference line ranges from [20 °,50 ° ]; and/or the exit angle (g) between the tangent of the variable inclination curve at the second end point (C) and the longitudinal reference line ranges from [57.7 °,70 ° ].
3. Impeller according to claim 2, characterized in that the inlet angle (d) is 50 ° and the outlet angle (g) is 57.7 °.
4. The impeller of claim 1, wherein the radius of curvature (R 1) of the first curve segment is 125mm and the radius of curvature (R 2) of the second curve segment is 38mm.
5. The impeller according to any one of claims 1 to 4, characterized in that the projection of the blade root (24) on the longitudinal projection plane is a second S-shaped curve.
6. The impeller according to claim 5, characterized in that the second S-shaped curve comprises a third end point (a) at the air inlet end side and a fourth end point (D) at the air outlet end side, wherein the inlet angle (m) between the tangent of the second S-shaped curve at the third end point (a) and the transverse reference line ranges from [65 °,120 ° ]; and/or the outlet angle (n) between the tangent of the second S-shaped curve at the fourth end point (D) and the transverse reference line ranges from [10 °,65 ° ].
7. Impeller according to claim 6, characterized in that the entry angle (m) between the tangent of the second S-shaped curve at the third end point (a) and the transverse reference line is 91 °, and the entry angle (n) between the tangent of the second S-shaped curve at the fourth end point (D) and the transverse reference line is 24 °.
8. An impeller according to any one of claims 1-4, characterized in that the blade (2) further comprises a leading edge (21) on the side of the air inlet end, the contour of the leading edge (21) being projected as a concave curve on a transverse projection plane perpendicular to the axis (L).
9. The impeller according to any one of claims 1 to 4, characterized in that the blade (2) is a twisted blade, the surface of which comprises a first curved surface section, a second curved surface section and a third curved surface section arranged in this order from the air inlet end to the air outlet end, the second curved surface section being located between the first curved surface section and the third curved surface section and being recessed to the rotation direction side of the impeller with respect to the first curved surface section and the third curved surface section.
10. The impeller of claim 9, wherein the first, second and third curved surface sections are transitioned through an arcuate surface.
11. The impeller according to any one of claims 1 to 4, characterized in that the blade (2) further comprises a trailing edge (23) at the side of the air outlet end, the projection of the contour of the trailing edge (23) on the longitudinal projection plane being a concave arc.
12. Impeller according to claim 1, characterized in that the number of blades (2) is 6 to 20.
13. A mixed flow fan comprising an impeller according to any one of claims 1 to 12.
14. An air conditioner comprising the mixed flow fan as claimed in claim 13.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010063828.7A CN111156191B (en) | 2020-01-20 | 2020-01-20 | Impeller, mixed flow fan and air conditioner |
| PCT/CN2020/139097 WO2021147606A1 (en) | 2020-01-20 | 2020-12-24 | Impeller, mixed flow blower and air conditioner |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202010063828.7A CN111156191B (en) | 2020-01-20 | 2020-01-20 | Impeller, mixed flow fan and air conditioner |
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| CN111156191A CN111156191A (en) | 2020-05-15 |
| CN111156191B true CN111156191B (en) | 2024-10-29 |
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| CN202010063828.7A Active CN111156191B (en) | 2020-01-20 | 2020-01-20 | Impeller, mixed flow fan and air conditioner |
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| CN (1) | CN111156191B (en) |
| WO (1) | WO2021147606A1 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111255738A (en) * | 2020-01-20 | 2020-06-09 | 珠海格力电器股份有限公司 | Impeller, mixed flow fan and air conditioner |
| 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 |
| CN111441984A (en) * | 2020-01-20 | 2020-07-24 | 珠海格力电器股份有限公司 | Impeller, mixed flow fan and air conditioner |
| CN112283800A (en) * | 2020-09-16 | 2021-01-29 | 珠海格力电器股份有限公司 | Machine and air conditioner in air conditioning |
| CN112943687A (en) * | 2021-04-13 | 2021-06-11 | 浙江银轮机械股份有限公司 | Impeller and automobile air conditioner blower |
| CN114483619B (en) * | 2021-12-27 | 2024-10-29 | 卡富环球有限公司 | Mixed flow impeller, mixed flow fan, air purifier and household appliance |
Citations (1)
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| CN211501072U (en) * | 2020-01-20 | 2020-09-15 | 珠海格力电器股份有限公司 | Impeller, mixed flow fan and air conditioner |
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| CN2345758Y (en) * | 1998-05-13 | 1999-10-27 | 高歌 | Centrifugal pump impeller with twisted salix-leaf-type blade |
| JP3724413B2 (en) * | 2001-11-05 | 2005-12-07 | 松下電器産業株式会社 | Electric blower for electric vacuum cleaner and electric vacuum cleaner using the same |
| JP2004044409A (en) * | 2002-07-09 | 2004-02-12 | Mitsubishi Heavy Ind Ltd | Water turbine and runner therefor |
| JP4094495B2 (en) * | 2003-06-16 | 2008-06-04 | 株式会社東芝 | Francis-type runner |
| CA2488714A1 (en) * | 2004-11-30 | 2006-05-30 | General Electric Canada | Runner for francis type hydraulic turbine |
| JP5314441B2 (en) * | 2009-01-20 | 2013-10-16 | 日立三菱水力株式会社 | Centrifugal hydraulic machine |
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| WO2014182121A1 (en) * | 2013-05-10 | 2014-11-13 | 엘지전자 주식회사 | Centrifugal fan and method for manufacturing same |
| KR101672262B1 (en) * | 2014-09-12 | 2016-11-03 | 한국에너지기술연구원 | Mixed flow impeller having airfoil cambered plate type backward twisted blades |
| CN106402020A (en) * | 2016-10-31 | 2017-02-15 | 广东威灵电机制造有限公司 | Impeller and fan having same |
| US10641282B2 (en) * | 2016-12-28 | 2020-05-05 | Nidec Corporation | Fan device and vacuum cleaner including the same |
| CN108252949A (en) * | 2018-01-29 | 2018-07-06 | 广东美的厨房电器制造有限公司 | Mixed flow wind wheel and flow-mixing blower fan |
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| CN111255738A (en) * | 2020-01-20 | 2020-06-09 | 珠海格力电器股份有限公司 | Impeller, mixed flow fan and air conditioner |
| 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 |
| 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 |
| CN211449177U (en) * | 2020-01-20 | 2020-09-08 | 珠海格力电器股份有限公司 | Impeller, mixed flow fan and air conditioner |
| CN111441984A (en) * | 2020-01-20 | 2020-07-24 | 珠海格力电器股份有限公司 | Impeller, mixed flow fan and air conditioner |
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2020
- 2020-01-20 CN CN202010063828.7A patent/CN111156191B/en active Active
- 2020-12-24 WO PCT/CN2020/139097 patent/WO2021147606A1/en active Application Filing
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| CN211501072U (en) * | 2020-01-20 | 2020-09-15 | 珠海格力电器股份有限公司 | Impeller, mixed flow fan and air conditioner |
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| CN111156191A (en) | 2020-05-15 |
| WO2021147606A1 (en) | 2021-07-29 |
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