CN217421631U - Mixed flow fan and ducted air conditioner - Google Patents
Mixed flow fan and ducted air conditioner Download PDFInfo
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- CN217421631U CN217421631U CN202221291361.2U CN202221291361U CN217421631U CN 217421631 U CN217421631 U CN 217421631U CN 202221291361 U CN202221291361 U CN 202221291361U CN 217421631 U CN217421631 U CN 217421631U
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- 230000006340 racemization Effects 0.000 description 5
- 230000002441 reversible effect Effects 0.000 description 5
- 238000004364 calculation method Methods 0.000 description 4
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Abstract
The utility model discloses a mixed flow fan and a duct machine, wherein the mixed flow fan comprises a volute; the impeller is arranged in the volute and comprises blades, and the maximum height of the blades in the axial direction of the impeller is H1; the rear guide vane structure is arranged at an air outlet of the volute, the maximum height of the rear guide vane structure in the axial direction of the impeller is H2, and the range of H2/H1 is 0.4-0.7. The utility model discloses a mixed flow fan can provide sufficient amount of wind and pressure through the ratio of the maximum height of adjusting back stator structure and the maximum height of blade in impeller axis direction, can increase fan efficiency with the area pressure performance of lower resistance's cost promotion fan.
Description
Technical Field
The utility model relates to a mixed flow fan technical field, concretely relates to mixed flow fan and tuber pipe machine.
Background
The air duct machine is one of air conditioners, in order to improve the comfortableness, some air duct machines adopt an upper cold air outlet mode and a lower hot air outlet mode, waterfall type refrigeration and carpet type warm air can be realized, in order to realize the air outlet mode, the air outlet of the air duct machine is required to be reversible, in the existing air outlet reversible air duct machine, a cross-flow fan and a centrifugal fan are generally adopted, but the fan is not reversible due to the problem of the setting mode of fan blades, the air direction after the reversal is not reversible, therefore, at least two fans can be arranged, one fan is responsible for forward air outlet, and the other fan is responsible for reverse air outlet, so that the structure of the air duct machine is larger, and the cost is higher.
In order to reduce the cost, the fan needs to be reduced, the mixed flow fan is a fan between the axial flow fan and the centrifugal fan, an impeller of the mixed flow fan enables air to do centrifugal motion and axial motion, and the air flow motion in the volute mixes two motion modes of axial flow and centrifugal motion, so that the mixed flow fan is called mixed flow. Moreover, the mixed flow fan not only can reduce the volume, but also can ensure the flow direction and the wind pressure of the airflow.
However, due to volume limitation, the air supply effect of the existing mixed flow fan is limited, and how to improve the air supply efficiency on the premise of the existing volume limitation is a problem to be solved urgently in the field.
SUMMERY OF THE UTILITY MODEL
The utility model discloses a mixed flow fan and tuber pipe machine has solved because volume restriction, the limited problem of current mixed flow fan's air supply effect.
According to the utility model discloses an aspect discloses a mixed flow fan, include: a volute; an impeller disposed inside the volute, the impeller including a blade having a maximum height in a direction of an axis of the impeller of H1; the rear guide vane structure is arranged at the air outlet position of the volute, the maximum height of the rear guide vane structure in the axial direction of the impeller is H2, and the range of H2/H1 is 0.4-0.7.
Further, a distance H3 is arranged between the rear guide vane structure and the impeller, and the range of H3/H1 is 0.1-0.3.
Further, the rear guide vane structure comprises a plurality of guide vanes, and all the guide vanes are annularly distributed by taking the axis of the impeller as an axis.
Further, at least one guide vane is provided with a swing shaft, the axis of the swing shaft and the axis of the impeller form an included angle, and the guide vane with the swing shaft can swing by taking the axis of the swing shaft as the axis.
Further, the included angle between the axis of the oscillating shaft and the axis of the impeller is 90 degrees.
Further, the oscillating angle of the guide vane ranges from 0 ° to 10 °.
Further, the mixed flow fan still includes: the flow collector is arranged at the air inlet of the volute, the flow collector is provided with a flow guide channel communicated with the interior of the volute, the flow guide channel is provided with an air flow inlet end and an air flow outlet end, the distance from the air flow inlet end to the air flow outlet end is H4, and the range of H4/H1 is 0.15-0.35.
Further, the flow guide channel is also provided with a contraction section, the contraction section is positioned between the airflow inlet end and the airflow outlet end, and the flow area of the contraction section is gradually reduced in the direction from the airflow inlet end to the airflow outlet end.
Further, in a direction from the airflow inlet end to the airflow outlet end, a change rate of reduction of the flow area of the contraction section is gradually reduced.
Further, in the direction from the airflow inlet end to the airflow outlet end, the change rate of the reduction of the flow area of the contraction section is unchanged.
Furthermore, the flow guide channel is also provided with a straight line section, the straight line section is connected with the contraction section, and the straight line section is positioned between the contraction section and the airflow outlet end.
Further, the blades comprise a plurality of long blades and a plurality of short blades, and the long blades and the short blades are alternately arranged at intervals.
According to the utility model discloses a second aspect discloses a tuber pipe machine, including foretell mixed flow fan.
The utility model discloses a mixed flow fan is through the ratio of the maximum height of adjustment back stator structure and the maximum height of blade at impeller axis direction, reasonable H2H 1's numerical value, can constitute the fan size of preferred performance, wherein reasonable size means that the impeller has sufficient working area, can provide sufficient amount of wind and pressure, it is reasonable also to mean stator size simultaneously, can promote the area pressure performance of fan with the cost of lower resistance, increase fan efficiency, cooperation between them, can make the fan area take the pressure ability to promote, the working efficiency promotes, can see out the amount of wind from the data and improve nearly 9.2%, the pressure head improves nearly 32.5%, the computational efficiency improves nearly 31.8%.
Drawings
Fig. 1 is a schematic structural view of a mixed flow fan according to a first embodiment of the present invention;
legend: 10. a volute; 11. an air outlet; 20. an impeller; 21. a blade; 30. a rear guide vane structure; 31. a guide vane; 40. a current collector; 41. a flow guide channel.
Detailed Description
The present invention is further illustrated by the following examples, but is not limited to the contents of the specification.
In the mixed flow fan in the prior art, a current collector 40 is usually disposed at an air inlet, and the current collector 40 can uniformly and smoothly guide air at an air inlet side into the mixed flow fan, so as to reduce flow loss and improve the efficiency of the mixed flow fan. Therefore, the structure of the collector 40 affects the performance of the mixed flow fan, the flow loss of the well-designed collector 40 is small, and the unreasonable design may deteriorate the inlet condition, resulting in the performance degradation.
At present, the structure of the current collector 40 is optimized more conventionally according to the height of the current collector 40, the size of the air inlet, the size of the air outlet, and the shape of the flow guide surface, although these improvements can improve the air supply efficiency of the mixed flow fan to some extent. However, through the research of the applicant on the flow principle of the airflow and the analysis of the simulation experiment data, the following results are found: this conventional improvement to the structural parameters of the collector 40 itself has very limited effect on the air flow of the mixed flow fan. The reason for this is that when the mixed flow fan is in operation, the process of the air flow entering the mixed flow fan and then being sent out by the mixed flow fan is a coherent whole process, so that when considering the improvement factor, the optimization of the parameters of the single component cannot be considered, and the problem of the matching between the parameters of the current collector 40 and the parameters of other components of the mixed flow fan is neglected. The matching between the parameters of the neglected current collector 40 and the parameters of other components of the mixed flow fan is an improvement point capable of effectively improving the air quantity of the mixed flow fan.
As shown in fig. 1, in a first embodiment of the present invention, a mixed flow fan is disclosed, which includes a volute 10, an impeller 20 and a rear guide vane structure 30, wherein the impeller 20 is disposed inside the volute 10, the impeller 20 includes a blade 21, and a maximum height of the blade 21 in an axial direction of the impeller 20 is H1; the rear guide vane structure 30 is arranged at the position of an air outlet 11 of the volute 10, the maximum height of the rear guide vane structure 30 in the axial direction of the impeller 20 is H2, and the range of H2/H1 is 0.4-0.7.
The utility model discloses a mixed flow fan is through being 0.4 ~ 0.7 with H2H 1's scope, in this embodiment, back stator structure 30 is in the maximum height of impeller 20 axis direction is H2, that is to say, H2 is the maximum height of back stator structure 30, H1 is the maximum height of blade 21 in impeller 20 axis direction, two dimensional change can conflict each other, the promotion of impeller 20 promptly can reduce the size of stator 31 must, and because the restriction of overall dimension, under the unchangeable condition of fan appearance basic dimension, reasonable size setting is the key that above-mentioned fan performance promoted, under both reasonable ratio, mixed flow fan can obtain comparatively outstanding performance data, the simulation data is as follows:
according to the simulation data, the utility model discloses a mixed flow fan is through the ratio of the maximum height of adjustment back stator structure 30 and the maximum height of blade 21 at impeller 20 axis direction, reasonable H2H 1's numerical value, can constitute the fan size of superior performance, wherein reasonable size means that the impeller has sufficient working area, can provide sufficient amount of wind and pressure, it is reasonable also to mean the stator size simultaneously, can promote the area pressure performance of fan with the cost of lower resistance, increase fan efficiency, cooperation between them, can make the fan area pressure ability promote, the working efficiency promotes, can see out the amount of wind from the data and improve nearly 9.2%, the pressure head improves nearly 32.5%, the computational efficiency improves nearly 31.8%, the working ability of mixed flow fan has been improved greatly, make the efficiency of mixed flow fan higher.
Specifically, when the value of H2/H1 is 0.55, the sizes of the two are most reasonable, the airflow enters the guide vane 31 at a high dynamic pressure by the action of the impeller 20, the efficiency of converting the dynamic pressure into static pressure by the guide vane 31 is highest, the pressure bearing capacity of the fan is improved, and the matching of the two is not acceptable. Therefore, the air quantity and the pressure head of the mixed flow fan are improved, and the calculation efficiency is also improved. When H2/H1 is reduced to 0.4, the size of the guide vane 31 becomes small, the capacity of the guide vane 31 for converting dynamic pressure into static pressure is reduced, and the air volume, the pressure head and the efficiency of the mixed flow fan are all reduced. When the value of H2/H1 is reduced to 0.35, the size of the guide vane 31 is too small, the guide vane 31 cannot convert enough dynamic pressure into static pressure, the pressure bearing capacity of the fan is reduced, the air volume is attenuated, the efficiency of the fan is insufficient, and the fan cannot be used. When H2/H1 is increased to 0.7, the size of the guide vane 31 is increased, the size of the impeller 20 is reduced, the power capability of the fan is reduced, and the air volume, the pressure head and the efficiency are all reduced. When the value of H2/H1 is increased to 0.74, the guide vane 31 is oversized, the impeller 20 is undersized, the work capacity of the fan is insufficient, the pressure bearing capacity is reduced, and the overall efficiency of the fan is obviously reduced. Meanwhile, the guide vane 31 is large in size, so that the whole circulation resistance of the fan is increased, the flow loss is increased, the pressure capacity of the fan is reduced, the air quantity is attenuated, the efficiency of the fan is insufficient, and the condition that the fan cannot be used is achieved.
A distance H3 is arranged between the rear guide vane structure 30 and the impeller 20, and the range of H3/H1 is 0.1-0.3. In this embodiment, a distance H3 exists between the rear guide vane structure 30 and the impeller 20, and a value of H3/H1 is within a reasonable range, so that the francis fan can obtain more excellent performance data, and simulation data are as follows:
according to simulation data, the ratio of the distance between the rear guide vane structure 30 and the impeller 20 to the maximum height of the blade 21 in the axial direction of the impeller 20 and the reasonable H3/H1 value can ensure that the blade has enough work capacity and simultaneously has enough size racemization space, so that airflow with larger dynamic pressure can be sufficiently racemized into airflow with smaller dynamic pressure through a racemization section, and the airflow enters the guide vane to further improve the pressure capacity, under the condition that the volume of the whole mixed flow fan is limited, the air volume is improved by nearly 6.0%, the pressure head is improved by nearly 26.9%, the calculation efficiency is improved by nearly 18.3%, the work capacity of the mixed flow fan is greatly improved, and the efficiency of the mixed flow fan is higher.
Specifically, when the value of H3/H1 is 0.2, the high-speed rotating airflow generated by the impeller 20 enters the despinning section with a high dynamic pressure, and despinning is performed in the space of the despinning section, that is, a part of the rotating speed is properly eliminated, and the airflow is guided to the guide vane structure to continuously improve the pressure capacity, so that the air volume and the pressure head of the mixed flow fan are both improved, and the calculation efficiency is also improved. When the value of H3/H1 is reduced to 0.1, the despinning space is reduced, the high-speed airflow cannot be despinned fully in the despinning section, and the high-speed airflow enters the guide vane with a larger rotation angle, so that impact loss is caused, the flow loss is increased, and the air volume attenuation and the efficiency are reduced. When the value of H3/H1 is reduced to 0.07, the racemization space is too small, high-speed airflow hardly racemizes in a racemization section and enters a guide vane with a larger rotation angle, so that shock loss is increased, flow loss is greatly increased, air volume attenuation and efficiency are reduced, and the condition that the air volume cannot be used is achieved. And when the H3/H1 is increased to 0.3, the racemization space is increased, the size of the movable blade is reduced, the working area is reduced, the capacity of the fan is reduced, and the efficiency of the mixed flow fan is obviously reduced. When the increase of H3/H1 is 0.34, the rotation-eliminating space is too large, the movable blade is over small in size, the working area is insufficient, the capacity of the fan is reduced, the air volume and the pressure head of the mixed-flow fan are both reduced seriously, the efficiency of the mixed-flow fan is also reduced obviously, and the condition that the mixed-flow fan cannot be used is achieved.
Further, the rear guide vane structure 30 includes a plurality of guide vanes 31, and all the guide vanes 31 are distributed annularly with the axis of the impeller 20 as an axis.
Furthermore, at least one guide vane 31 is provided with a swinging shaft, the axis of the swinging shaft and the axis of the impeller 20 form an included angle, and the guide vane 31 with the swinging shaft can swing by taking the axis of the swinging shaft as the axis. The rear guide vane structure 30 is used for further guiding the outlet air of the impeller 20, and when the impeller 20 operates at different rotating speeds, the angle at which the gas exits the impeller 20 is different, i.e. the angle at which the gas enters the gap is different, the spacing is of a size such that its ability to racemize, i.e. to change the angle of the gas, when the gas angle into the pitch is different, so that the gas angle into the rear guide vane structure 30 is also different, in order to make the flow angle of the gas flow as identical as possible to the angle of the gas flow out of the pitch, through the swing of the guide vanes 31, the flow angle of the airflow at the rear guide vane structure 30 is changed, the fit degree of the airflow direction flowing out of the rear guide vane structure 30 is further increased, therefore, the increase of the exhaust uniformity of the mixed flow fan is facilitated, and the mixed flow fan can achieve the optimal air volume value and the optimal airflow driving performance under multiple working rotating speeds. Preferably, the greater the rotational speed of the blade, the greater the angle at which the airflow leaves the impeller 20, and therefore the greater the angle of inclination of the guide vane 31, and conversely, the smaller the rotational speed of the impeller 20, the smaller the angle of inclination of the guide vane 31.
The swing angle of the guide vane 31 ranges from 0 ° to 10 °. Preferably 0 ° to 5 °.
Wherein the angle between the axis of oscillation and the axis of the impeller 20 is 90 deg., i.e. the axes of both are perpendicular. So that no structural interference is generated with the volute 10 in the swinging process of the guide vane 31, and the structure reliability of the guide vane 31 and the volute 10 is ensured.
The mixed flow fan further comprises a current collector 40, the current collector 40 is arranged at an air inlet position of the volute 10, the current collector 40 is provided with a flow guide channel 41 communicated with the inside of the volute 10, and the flow guide channel 41 is provided with an air flow inlet end and an air flow outlet end.
The utility model discloses a mixed flow fan is 0.15 ~ 0.35 through the scope with H4H 1, in this embodiment, the air current entrance point of water conservancy diversion passageway 41 is H4 to the distance of air current exit end, that is to say, H4 is the length of the water conservancy diversion passageway 41 of collector 40, H1 is the maximum height of blade 21 in 20 axis directions of impeller, under the reasonable ratio between them, mixed flow fan can obtain comparatively outstanding performance data, the simulation data is as follows:
according to the simulation data, the utility model discloses a length and the blade 21 of mixed flow fan through the water conservancy diversion passageway 41 of adjustment collector 40 are at the ratio of the maximum height of impeller 20 axis direction, the air current gets into impeller 20 and participates in rotatory doing work via collector 40, suitable collector size can provide sufficient inflow area, further even incoming flow simultaneously, in order to reduce flow resistance, balanced collector 40 and impeller 20's size simultaneously, can furthest's the acting capacity of promotion fan blade, promote fan blade efficiency, thereby make the amount of wind improve nearly 8%, the pressure head improves nearly 13.8%, the computational efficiency improves nearly 11.8%, the acting capacity of mixed flow fan has been improved greatly, make the efficiency of mixed flow fan higher.
Specifically, when the value of H4/H1 is 0.25, the size of the current collector 40 and the impeller 20 is optimal, the current collector 40 can play an effective flow guiding role, the size of the impeller 20 can improve the pressure bearing capacity of the fan, and the airflow can smoothly and uniformly enter the impeller 20 while ensuring the air inflow, so that the air volume and the pressure head of the mixed flow fan are both improved, and the calculation efficiency is also improved. When the value of H4/H1 is reduced to 0.15, the size of the current collector 40 is reduced, the size of the impeller 20 is further increased, the flow guiding effect is reduced, and the power-applying capacity of the impeller 20 is increased, so that the reduction of the air volume and the efficiency of the fan and the improvement of the pressure-bearing capacity can be seen. When the value of H4/H1 is reduced to 0.10, the size of the current collector 40 is too small, the size of the impeller 20 is too large, and the current collector 40 is difficult to play a role in guiding flow, so that the air volume and the pressure head of the mixed flow fan are both seriously reduced, the efficiency of the mixed flow fan is also obviously reduced, and the mixed flow fan can not be used. When the value of H4/H1 is increased to 0.35, the size of the impeller 20 is reduced, the work area of the impeller 20 is reduced, and the air volume, the pressure head and the efficiency of the fan are reduced. When H4/H1 is continuously increased to 0.4, the size of the current collector is overlarge at the moment, the size of the impeller 20 is further compressed, the working area of the impeller 20 is seriously insufficient, the working function of the impeller 20 is reduced, the air volume and the pressure head of the mixed flow fan are both seriously reduced, the efficiency of the mixed flow fan is also obviously reduced, and the mixed flow fan can not be used.
As shown in fig. 1, the flow guide channel 41 further has a constricted section located between the air flow inlet end and the air flow outlet end, and the flow area of the constricted section gradually decreases from the air flow inlet end to the air flow outlet end. Because the flow area of the contraction section of the flow guide channel 41 is gradually reduced, a gradually-reduced flow channel is formed, the airflow is accelerated, and a uniform velocity field and a uniform pressure field are formed, so that the flow loss is reduced, and the efficiency of the mixed flow fan is improved.
In the direction from the air flow inlet end to the air flow outlet end, the change rate of the reduction of the flow area of the contraction section is gradually reduced. That is to say, the inner wall of the flow guiding channel 41 located at the contraction section is an arc-shaped inner wall, and along the direction from the air flow inlet end to the air flow outlet end, the radian of the inner wall is gradually reduced, and the air flow is converged to the outlet of the flow collector 40 by the inlet of the flow collector 40 under the action of the arc line of the inner wall of the flow collector 40, so that the arc can not only guide the air flow, but also reduce the flow resistance of the section to a certain extent, and play a role in increasing the air volume.
In another embodiment, not shown, the rate of change of the reduction of the flow area of the constrictor is constant from the inlet end to the outlet end of the airflow. That is, the inner wall of the flow guiding channel 41 located at the contracting section is a plane, and in the direction from the air flow inlet end to the air flow outlet end, the straight line section can also play the role of guiding and gathering the air flow like an arc, and the processing is simple and easy, and the cost is low.
In the first embodiment shown in the figure, the flow guide channel 41 further has a straight section connected to the convergent section, the straight section being located between the convergent section and the gas flow outlet end. The straight line section is positioned at the tail part of the current collector 40, the polymerized gas flows more disorderly, and the straight line section can inhibit the mixed flow, so that the air inlet condition of the mixed flow fan is improved to a certain extent.
Further, the blades 21 include a plurality of long blades and a plurality of short blades, and the long blades and the short blades are alternately spaced. The long blades and the short blades are alternately arranged at intervals, so that the number of the blades 21 doing work in the impeller 20 is increased, the pressure capacity is improved, meanwhile, the circulation resistance of air flow is not increased, the air volume is not reduced, and the performance of the fan is ensured.
According to the utility model discloses a second aspect discloses a tuber pipe machine, including foretell mixed flow fan.
It is to be understood that the above-described embodiments of the present invention are merely examples provided for clearly illustrating the present invention, and are not intended to limit the embodiments of the present invention. Other variations and modifications will be apparent to persons skilled in the art in light of the above description. Not all embodiments are exhaustive. All obvious changes or variations led out by the technical scheme of the utility model are still in the protection scope of the utility model.
Claims (13)
1. A mixed flow fan, comprising:
a volute (10);
an impeller (20), wherein the impeller (20) is arranged inside the volute (10), the impeller (20) comprises a blade (21), and the maximum height of the blade (21) in the axial direction of the impeller (20) is H1;
rear guide vane structure (30), rear guide vane structure (30) set up the air outlet position department of spiral case (10), rear guide vane structure (30) are in the maximum height of impeller (20) axis direction is H2, and H2/H1's scope is 0.4 ~ 0.7.
2. The mixed flow fan of claim 1,
a distance H3 is arranged between the rear guide vane structure (30) and the impeller (20), and the range of H3/H1 is 0.1-0.3.
3. The mixed flow fan of claim 1,
the rear guide vane structure (30) comprises a plurality of guide vanes (31), and all the guide vanes (31) are annularly distributed by taking the axis of the impeller (20) as an axis.
4. The mixed flow fan of claim 3,
at least one guide vane (31) is provided with a swinging shaft, the axis of the swinging shaft and the axis of the impeller (20) form an included angle, and the guide vane (31) with the swinging shaft can swing by taking the axis of the swinging shaft as the axis.
5. The mixed flow fan of claim 4,
the included angle between the axial line of the swinging shaft and the axial line of the impeller (20) is 90 degrees.
6. The mixed flow fan of claim 5,
the range of the swing angle of the guide vane (31) is 0 DEG to 10 deg.
7. The mixed flow fan of claim 1 further comprising:
the flow collector (40) is arranged at an air inlet position of the volute (10), the flow collector (40) is provided with a flow guide channel (41) communicated with the interior of the volute (10), the flow guide channel (41) is provided with an air flow inlet end and an air flow outlet end, the distance from the air flow inlet end to the air flow outlet end is H4, and the range of H4/H1 is 0.15-0.35.
8. The mixed flow fan of claim 7,
the flow guide channel (41) is also provided with a contraction section, the contraction section is positioned between the airflow inlet end and the airflow outlet end, and the flow area of the contraction section is gradually reduced in the direction from the airflow inlet end to the airflow outlet end.
9. The mixed flow fan of claim 8,
in the direction from the airflow inlet end to the airflow outlet end, the change rate of the reduction of the flow area of the contraction section is gradually reduced.
10. The mixed flow fan of claim 8,
and in the direction from the airflow inlet end to the airflow outlet end, the change rate of the reduction of the flow area of the contraction section is unchanged.
11. The mixed flow fan of claim 10,
the flow guide channel (41) is further provided with a straight line section, the straight line section is connected with the contraction section, and the straight line section is located between the contraction section and the airflow outlet end.
12. The mixed flow fan of claim 1,
the blades (21) comprise a plurality of long blades and a plurality of short blades, and the long blades and the short blades are alternately arranged at intervals.
13. A duct machine comprising a mixed flow fan as claimed in any one of claims 1 to 12.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202221291361.2U CN217421631U (en) | 2022-05-27 | 2022-05-27 | Mixed flow fan and ducted air conditioner |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202221291361.2U CN217421631U (en) | 2022-05-27 | 2022-05-27 | Mixed flow fan and ducted air conditioner |
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| CN217421631U true CN217421631U (en) | 2022-09-13 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2023226363A1 (en) * | 2022-05-27 | 2023-11-30 | 珠海格力电器股份有限公司 | Mixed flow fan and duct type air conditioner |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2023226363A1 (en) * | 2022-05-27 | 2023-11-30 | 珠海格力电器股份有限公司 | Mixed flow fan and duct type air conditioner |
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