CN217421629U - Mixed flow fan and ducted air conditioner - Google Patents
Mixed flow fan and ducted air conditioner Download PDFInfo
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- CN217421629U CN217421629U CN202221287803.6U CN202221287803U CN217421629U CN 217421629 U CN217421629 U CN 217421629U CN 202221287803 U CN202221287803 U CN 202221287803U CN 217421629 U CN217421629 U CN 217421629U
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Abstract
The utility model discloses a mixed flow fan and tuber pipe machine, mixed flow fan includes: a volute; the current collector is arranged at the position of an air inlet of the volute and is provided with a flow guide channel communicated with the interior of the volute, and the inner diameter of an airflow inlet end of the flow guide channel is D1; the impeller is arranged in the volute, the maximum diameter of the impeller is D2, and the range of D1/D2 is 0.8-0.9. The utility model discloses a mixed flow fan is through the ratio of the maximum outlet diameter of the air current entrance point internal diameter of adjustment water conservancy diversion passageway and impeller, make the air current at collector and the impeller in-process of flowing through, the resistance that meets is littleer, the turbulent flow of production still less, under the limited condition of whole mixed flow fan volume, make the amount of wind improve nearly 6%, the pressure head improves nearly 8%, the computational efficiency improves nearly 6%, the power capacity of mixed flow fan has been improved greatly, the efficiency of messenger mixed flow fan is higher.
Description
Technical Field
The utility model relates to an air treatment equipment 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 a mode of discharging cold air upwards and discharging hot air downwards, thus waterfall type refrigeration and carpet type warm air can be realized, in order to realize the air-out mode, the air-out of the air duct machine is required to be reversible, in the existing air-out reversible air duct machine, a cross-flow mixed flow fan and a centrifugal mixed flow fan are usually adopted, but the mixed flow fan has the problem that the wind direction cannot be reversed after reversal due to the arrangement mode of mixed flow fan blades, therefore, only at least two mixed flow fans are arranged, one fan is responsible for forward air-out, and the other fan is responsible for reverse air-out, so that the structure of the pipe mixed flow fan is larger, and the cost is higher.
In order to reduce the cost, a mixed flow fan needs to be reduced, the mixed flow fan is a mixed flow fan between an axial flow mixed flow fan and a centrifugal mixed flow fan, an impeller of the mixed flow fan enables air to do centrifugal motion and axial motion, and the air flow motion in a volute mixes the axial flow motion and the 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; the flow collector is arranged at the air inlet position of the volute, the flow collector is provided with a flow guide channel communicated with the interior of the volute, and the inner diameter of the air flow inlet end of the flow guide channel is D1; the impeller is arranged inside the volute, the maximum diameter of the impeller is D2, and the range of D1/D2 is 0.8-0.9.
Furthermore, the flow guide channel is also provided with an airflow outlet end, the inner diameter of the flow guide channel at the airflow outlet end is D3, and the range of D1/D3 is 1.2-1.
Further, the distance from the air flow inlet end to the air flow outlet end is H1, and the range of H1/D2 is 0.1-0.3.
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 impeller comprises blades, the maximum height of the blades in the axial direction of the impeller is H2, and the range of H2/D2 is 0.38-0.48.
Further, the impeller also comprises an impeller cover, an airflow channel is formed inside the impeller cover, and the blades are positioned in the airflow channel; the airflow channel is provided with an expansion section, the expansion section is positioned between the air inlet end of the airflow channel and the air outlet end of the airflow channel, and the flow area of the expansion section is gradually increased in the direction from the air inlet end of the airflow channel to the air outlet end of the airflow channel.
Further, an air outlet is also formed in the volute; the distance between the airflow inlet end of the flow guide channel and the air outlet is A, and the ratio range of H2/A is 0.37-0.47.
Further, along the radial direction of the impeller, the maximum diameter of the volute is B, and the ratio of B/D2 ranges from 1.1 to 1.25.
Furthermore, the center of the airflow inlet end of the flow guide channel and the center connecting line of the air outlet are collinear with the axis of the impeller.
Further, the surface of the blade is provided with pits and/or projections.
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 outlet diameter of the air current entrance point internal diameter of adjustment water conservancy diversion passageway and impeller, make the air current at collector and the impeller in-process of flowing through, the resistance that meets is littleer, the turbulent flow of production still less, under the limited condition of whole mixed flow fan volume, make the amount of wind improve nearly 6%, the pressure head improves nearly 8%, the computational efficiency improves nearly 6%, the power capacity of mixed flow fan has been improved greatly, the efficiency of messenger mixed flow fan is higher.
Drawings
Fig. 1 is a schematic structural view of a mixed flow fan according to a first embodiment of the present invention;
fig. 2 is a schematic structural diagram of an impeller of a mixed flow fan according to a first embodiment of the present invention;
fig. 3 is a schematic structural diagram of a current collector of a mixed flow fan according to a second embodiment of the present invention;
legend: 10. a volute; 11. an air outlet; 20. a current collector; 21. a flow guide channel; 30. an impeller; 31. a blade; 32. and (4) a wheel cover.
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 is usually arranged at an air inlet, and the current collector 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 affects the performance of the mixed flow fan, the flow loss of the well-designed collector is small, and the unreasonable design can deteriorate the inlet condition, so that the performance is reduced.
At present, the structure of the current collector is optimized more conventionally according to the height of the current collector, the size of the air inlet, the size of the air outlet and the shape of the flow guide surface, although the improvement can improve the air supply efficiency of the mixed flow fan to a certain 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: such conventional improvements to the structural parameters of the current collector have had very limited impact on the air flow of mixed flow fans. The reason is that when the mixed flow fan runs, the process that airflow enters the mixed flow fan and then is sent out by the mixed flow fan is a coherent integral process, so that when improvement factors are considered, the optimization of the self parameters of a single component cannot be considered, and the matching problem between the parameters of the current collector and the parameters of other components of the mixed flow fan is ignored. The matching between the parameters of the neglected current collector and the parameters of other parts of the mixed flow fan is an improvement point capable of effectively improving the air quantity of the mixed flow fan.
For the above reasons, as shown in fig. 1 and fig. 2, in the first embodiment of the present invention, a mixed flow fan is disclosed, which includes a spiral casing 10, a current collector 20 and an impeller 30, wherein the current collector 20 is connected to the spiral casing 10, the current collector 20 is disposed at an air inlet of the spiral casing 10, the current collector 20 has a flow guiding channel 21 communicated with the inside of the spiral casing 10, and an inner diameter of an air flow inlet end of the flow guiding channel 21 is D1; the impeller 30 is arranged inside the volute 10, the maximum diameter of the impeller 30 is D2, and the range of D1/D2 is 0.8-0.9.
The utility model discloses a mixed flow fan is 0.8 ~ 0.9 through the scope with D1D 2, and in this embodiment, the internal diameter of the air current entrance point of water conservancy diversion passageway 21 is D1, that is to say, D1 is the entrance diameter of whole mixed flow fan, and D2 is impeller 30's maximum exit diameter, and under the reasonable ratio in two, the mixed flow fan can obtain comparatively outstanding performance data, and the emulation data is as follows:
| D1/D2 | rotational speed (rpm) | Calculating air volume (m) 3 /h) | Calculating pressure head (Pa) | Calculated efficiency (%) |
| 0.78 | 2200 | 482 | 84.9 | 64.7 |
| 0.80 | 2200 | 501 | 86.3 | 67.2 |
| 0.84 | 2200 | 510 | 90.4 | 69.1 |
| 0.90 | 2200 | 498 | 87.9 | 66.3 |
| 0.93 | 2200 | 485 | 83.5 | 64.3 |
According to simulation data, when the value of D1/D2 is between 0.8 and 0.9, the air flow can stably and uniformly enter the impeller 30 while ensuring the air inflow, so that the air flow has smaller resistance and generates less turbulence in the process of flowing through the current collector 20 and the impeller 30, and the air inflow resistance of the impeller 30 is reduced, therefore, the work performance of the impeller 30 is increased, the air volume and the pressure head of the mixed flow fan are both improved, and the calculation efficiency is also improved, wherein when the value of D1/D2 is 0.84, the air inflow is larger, but the generated turbulence is the least, the air inflow resistance of the impeller 30 is the least, so that the air volume, the pressure head and the calculation efficiency are obviously improved, the air volume is improved by nearly 6%, the pressure head is improved by nearly 8%, and the calculation efficiency is improved by nearly 6%; when the D1/D2 is reduced to 0.78, the flow surface of the air inlet end of the airflow is reduced too much, and the air inlet amount is influenced, so that 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 obviously reduced, and the mixed flow fan can not be used; when the D1/D2 is increased to 0.93, the air inflow is guaranteed, so that the impeller 30 is too large in size, the uniform airflow field cannot completely cover the impeller 30, more turbulence is generated, the resistance is increased, the work function of the impeller 30 is reduced, the air volume and the pressure head of the mixed flow fan are both reduced seriously, and the efficiency of the mixed flow fan is also reduced obviously.
The utility model discloses a mixed flow fan is through the ratio of the maximum exit diameter of the air current entrance point internal diameter of adjustment water conservancy diversion passageway 21 and impeller 30, make the air current at flow collector 20 and impeller 30 in-process, the air flow improves, the resistance that meets is littleer, the turbulent flow of production still less, under the limited condition of whole mixed flow fan volume, thereby make the amount of wind improve nearly 6%, the pressure head improves nearly 8%, the computational efficiency improves nearly 6%, the power-doing ability of mixed flow fan has been improved greatly, the efficiency of messenger mixed flow fan is higher.
Furthermore, the flow guide channel 21 is also provided with an air flow outlet end, the inner diameter of the flow guide channel 21 at the air flow outlet end is D3, and the range of D1/D3 is 1.2-1. The utility model discloses a mixed flow fan is 1.2 ~ 1 through the scope with D1D 3, to collector 20, D1's size generally will be greater than D3's size, but in order to guarantee the rotatable function of mixed flow fan, if D1D 3's value is bigger than normal the external dimension that will enlarge mixed flow fan, influence overall layout, and D1D 3's value is little then can not play the effect of mass flow, mixed flow fan performance also can descend. The simulation test is carried out on the mixed flow fan of the embodiment, the numerical value of the mixed flow fan D1/D3 is changed, and the simulation result is as follows:
| D1/D3 | rotational speed (rpm) | Calculating air volume (m) 3 /h) | Calculating pressure head (Pa) | Calculated efficiency (%) |
| 1.15 | 2200 | 510 | 90.4 | 69.1 |
| 1.00 | 2200 | 476 | 83.6 | 65.2 |
| 0.99 | 2200 | 460 | 82.1 | 64.3 |
According to simulation data, when the value of D1/D3 is larger than 1.2, the overall layout of the mixed flow fan is influenced, so that the consideration is not given; when the value of D1/D3 is 1.15, the air flow enters the impeller 30 stably and uniformly while ensuring the air inflow, so that the air flow has the smallest resistance and the smallest turbulent flow generated in the process of flowing through the current collector 20 and the impeller 30, and the air inflow resistance of the impeller 30 is obviously reduced, therefore, the work function of the impeller 30 is strongest, the air volume and the pressure head of the mixed flow fan are the largest, and the efficiency of the mixed flow fan is also the highest; when the D1/D3 is reduced to 1.00, the size of the air inlet end is reduced, the air inlet amount is influenced, and the air inlet resistance is seriously increased, so that the air volume and the pressure head of the mixed flow fan are obviously reduced, and the efficiency of the mixed flow fan is also obviously reduced; when the value of D1/D3 is reduced to 0.99, the current collector 20 cannot perform the current collecting function, and as can be seen from the above table, the air volume attenuation of the mixed flow fan is serious, and the efficiency of the pressure head and the mixed flow fan is far lower than the data with the ratio of 1.15.
It should be noted that when the value of D1/D2 is 0.8-0.9, and the value of D1/D3 is 1.2-1, the uniform velocity field generated by the current collector 20 can completely cover the rotation range of the impeller 30, so that the airflow resistance at each position is relatively average when the impeller 30 rotates, and the local resistance is prevented from being too large when the impeller 30 rotates, so that the air volume and pressure head of the mixed flow fan are obviously increased, and the efficiency of the mixed flow fan is obviously improved.
The utility model discloses a mixed flow fan is through optimizing the internal diameter of water conservancy diversion passageway air current entrance point and airflow outlet end's internal diameter relation, makes the air current at the in-process that flows through collector water conservancy diversion passageway 10, and the resistance that meets is littleer, and the turbulent flow that produces still less, under the limited condition of whole mixed flow fan volume to make the amount of wind improve nearly 11%, the pressure head improves 10%, and computational efficiency improves nearly 5%, has improved the power capacity of mixed flow fan greatly, makes the efficiency of mixed flow fan higher. Moreover, because the air quantity is increased under the condition of the same rotating speed, correspondingly, under the condition of the same air quantity, the rotating speed can be reduced, thereby reducing the noise brought by the rotating process.
Furthermore, the distance from the air flow inlet end to the air flow outlet end is H1, and the range of H1/D2 is 0.1-0.3. The utility model discloses a mixed flow fan sets up to 0.1 ~ 0.3 through the scope with H1D 2, and the high H1 of collector 20 is for impeller 30 maximum diameter D2, and too high H1 can influence the overall arrangement distribution of mixed flow fan, and H1 is little then can increase the air inlet loss of mixed flow fan, influences mixed flow fan performance. The simulation test is carried out on the mixed flow fan of the embodiment, the numerical value of the mixed flow fan H1/D2 is changed, and the simulation result is as follows:
| H1/D2 | rotational speed (rpm) | Calculating air volume (m) 3 /h) | Calculating pressure head (Pa) | Calculated efficiency (%) |
| 0.35 | 2200 | 495 | 86.1 | 62.9 |
| 0.30 | 2200 | 498 | 87.6 | 64.7 |
| 0.20 | 2200 | 504 | 88.2 | 67.5 |
| 0.12 | 2200 | 510 | 90.4 | 69.1 |
| 0.09 | 2200 | 496 | 85.5 | 61.4 |
According to simulation data, when the range of H1/D2 is 0.1-0.3, airflow can stably and uniformly enter the impeller 30, so that the airflow encounters smaller resistance and generates less turbulence in the process of flowing through the current collector 20 and the impeller 30, and the air inlet resistance of the impeller 30 is reduced, therefore, the work-doing capacity of the impeller 30 is increased, the air volume and the pressure head of the mixed flow fan are improved, and the calculation efficiency is also improved, wherein when the value of H1/D2 is 0.12, the flow field formed by the airflow is most stable and uniform, the generated turbulence is least, the air inlet resistance of the impeller 30 is least, and therefore, the air volume, the pressure head and the calculation efficiency are obviously improved; when the H1/D2 is reduced to 0.09, the current collector 20 is difficult to play an effective current collecting role, the air inflow is influenced, and the air inflow is attenuated by about 3 percent, so that the air volume and the pressure head of the mixed flow fan are both seriously reduced, and the efficiency of the mixed flow fan is also obviously reduced; when the H1/D2 is increased to 0.35, the current collector 20 extrudes the size space of the impeller 30, the performance of the fan blade is reduced, the air volume and the pressure head of the mixed flow fan are both reduced seriously, and the efficiency of the mixed flow fan is also reduced obviously.
As shown in fig. 1, the flow guide channel 21 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 21 is gradually reduced, a gradually reduced flow channel is formed, the air flow is accelerated, and a uniform speed 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 diversion channel 21 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, the air flow is converged to the outlet of the flow collector 20 from the inlet of the flow collector 20 under the action of the inner wall arc of the flow collector 20, the arc can not only guide the air flow, but also reduce the flow resistance of the section to a certain extent, and the effect of improving the air volume is achieved.
In the second embodiment shown in fig. 3, the rate of change of the reduction of the flow area of the constriction section is constant from the gas flow inlet end to the gas flow outlet end. That is, the inner wall of the flow guiding channel 21 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 fig. 1, the flow guide channel 21 further has a straight section, the straight section is connected to the contracting section, and the straight section is located between the contracting section and the air flow outlet end. The straight line section is positioned at the tail part of the current collector, 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.
As shown in FIGS. 1 and 3, the impeller 30 includes the blades 31, the maximum height of the blades 31 in the axial direction of the impeller 30 is H2, and the range of H2/D2 is 0.38-0.48. The value of H2/D2 also affects the basic layout of the whole mixed flow fan, when the value of H2/D2 is smaller, because the height of H2 of the impeller 30 is insufficient, an effective supercharging channel cannot be formed, the impeller 30 cannot perform sufficient diffusion on the gas, the pressure bearing capacity of the mixed flow fan is insufficient, and the blade profile of the blade 31 is more biased to the axial flow; when the value of H2/D2 is larger, a great deal of radial space is wasted to meet the rotation requirement, and the basic size of the gas part of the mixed flow fan is influenced. The simulation test is carried out on the mixed flow fan of the embodiment, the numerical value of the mixed flow fan H2/D2 is changed, and the simulation result is as follows:
| H2/D2 | rotating speed (rpm) | Calculating air volume (m) 3 /h) | Impeller head (Pa) | Impeller efficiency (%) |
| 0.38 | 2200 | 501 | 114.3 | 78.3 |
| 0.40 | 2200 | 510 | 126.8 | 87.1 |
| 0.48 | 2200 | 503 | 115.4 | 79.2 |
| 0.50 | 2200 | 497 | 111.9 | 74.6 |
According to simulation data, when the range of H2/D2 is 0.38-0.48, the impeller 30 can form an effective supercharging channel, the impeller 30 can perform sufficient diffusion on gas, so that the under-pressure capacity of the mixed flow fan is improved, the air volume and the pressure head of the mixed flow fan are both improved, and the calculation efficiency is also improved, wherein when the value of H2/D2 is 0.12, the diffusion effect of the impeller 30 on the gas is the best, the under-pressure capacity of the mixed flow fan is the highest, and therefore the air volume, the pressure head and the calculation efficiency are obviously improved; when the H2/D2 is less than 0.38, the H2 height of the impeller 30 is insufficient, an effective pressurizing channel cannot be formed, the impeller 30 cannot perform sufficient diffusion on gas, and the pressure capacity of the mixed flow fan is insufficient, so that the air volume and the pressure head of the mixed flow fan are both reduced seriously, and the efficiency of the mixed flow fan is also obviously reduced; when the H2/D2 is increased to 0.50, the performance of the impeller 30 is reduced on the contrary, so that 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, in addition, after the size is increased, a great radial space is wasted to meet the rotation requirement, and the basic size of the air part of the mixed flow fan is influenced.
The impeller 30 further comprises an impeller cover 32, an airflow channel is formed inside the impeller cover 32, and the blades 31 are located in the airflow channel; the air flow channel is provided with an expansion section, the expansion section is positioned between the air inlet end of the air flow channel and the air outlet end of the air flow channel, and the flow area of the expansion section is gradually increased in the direction from the air inlet end of the air flow channel to the air outlet end of the air flow channel. Through setting up the expansion section, can improve the static pressure of air current to improve mixed flow fan work efficiency.
The volute 10 is also provided with an air outlet 11; the distance between the airflow inlet end of the flow guide channel 21 and the air outlet 11 is A, and the ratio range of H2/A is 0.37-0.47. The distance a can also be understood as the length of the scroll casing 10, and in the vertical direction shown in fig. 1, the length of the scroll casing 10 is a. The simulation test is carried out on the mixed flow fan of the embodiment, the numerical value of the mixed flow fan H2/A is changed, and the simulation result is as follows
| H2/A | Rotational speed (rpm) | Calculating air volume (m) 3 /h) | Impeller pressure head (Pa) | Diffusion loss (Pa) |
| 0.30 | 2200 | 468 | 91.4 | 49.6 |
| 0.35 | 2200 | 482 | 104.3 | 41.3 |
| 0.41 | 2200 | 510 | 126.8 | 36.2 |
| 0.48 | 2200 | 493 | 121.9 | 62.1 |
| 0.52 | 2200 | 485 | 116.7 | 73.3 |
According to simulation data, when the range of H2/A is 0.35-0.48, the impeller 30 has a large working surface on airflow, and the under-pressure capability of the mixed flow fan is ensured, so that the air volume and the pressure head of the mixed flow fan are both improved, and the diffusion loss is reduced, wherein when the value of H2/A is 0.41, the under-pressure capability of the mixed flow fan is strongest, so that the air volume and the pressure head are obviously improved, and the diffusion loss is obviously reduced; when the H2/A is reduced to 0.30, the working area of the impeller 30 is insufficient, which leads to the insufficient under-pressure capability of the mixed flow fan, therefore, the air volume and pressure head of the mixed flow fan are both reduced seriously, and the diffusion loss is increased obviously; when the H2/A is increased to 0.52, the mixed flow fan is difficult to effectively convert the high dynamic pressure generated by the impeller 30 into static pressure, and the pressure bearing capacity of the mixed flow fan is deficient, so that the air volume and the pressure head of the mixed flow fan are both seriously reduced, and the diffusion loss is obviously increased.
Because the mixed flow fan of this embodiment is set up in the tuber pipe machine, so there is technological requirement and structure cooperation requirement to the size shape of mixed flow fan's spiral case 10, consequently, make further improvement to mixed flow fan's spiral case 10, when satisfying the above-mentioned requirement of tuber pipe machine, maximize the amount of wind that promotes mixed flow fan. In the present embodiment, the maximum diameter of the volute 10 in the radial direction of the impeller 30 is B, and the ratio of B/D2 is in the range of 1.1-1.25. Referring to fig. 1, the maximum diameter B of the volute 10 directly determines the shape of the volute of the mixed flow fan, and the value of the maximum diameter B also has a corresponding relationship with the impeller 30, that is, the gap between the impeller 30 and the volute in the radial direction is controlled within a certain range, so as to improve the air volume of the mixed flow fan. The simulation test is carried out on the mixed flow fan of the embodiment, the numerical value of the B/D2 of the mixed flow fan is changed, and the simulation result is as follows
| B/D2 | Rotational speed (rpm) | Calculating air volume (m) 3 /h) | Impeller head (Pa) | Diffusion loss (Pa) |
| 1.04 | 2200 | 496 | 123.4 | 58.4 |
| 1.10 | 2200 | 502 | 124.6 | 50.3 |
| 1.19 | 2200 | 510 | 126.8 | 36.2 |
| 1.25 | 2200 | 504 | 123.7 | 47.6 |
| 1.30 | 2200 | 498 | 120.3 | 53.1 |
The air flow applies work through the impeller 30, high dynamic pressure is initially provided, the dynamic pressure needs enough space to be released, and a part of the dynamic pressure is converted into static pressure to continue flowing, according to simulation data, when the range of B/D2 is 1.1-1.25, the pressure release space is sufficient, the proportion of the dynamic pressure converted into the static pressure is large, so that the air volume and the pressure head of the mixed flow fan are large, and the diffusion loss is small, wherein when the value of B/D2 is 1.19, the proportion of the dynamic pressure converted into the static pressure is maximum, so that the air volume and the pressure head of the mixed flow fan are obviously improved, and the diffusion loss is obviously reduced; when the B/D2 is reduced to 1.04, the pressure release space is insufficient, and the proportion of converting dynamic pressure into static pressure is small, so that the air volume and the pressure head of the mixed flow fan are both reduced seriously, and the diffusion loss is also increased obviously; when the B/D2 is increased to 1.30, the performance of the fan blade is reduced, the air volume and pressure head of the mixed flow fan are both reduced seriously, the diffusion loss is obviously increased, the overall size of the mixed flow fan is further enlarged, the basic size of other components is compressed, and the improvement of the performance of the mixed flow fan is not facilitated.
Preferably, the volute 10 of the mixed flow fan in this embodiment is of a table structure, the maximum diameter of the volute 10 is equal to the diameter of the table structure, and the volute 10 is located at two bottom surfaces of the table structure and is the airflow inlet end and the air outlet 11 of the diversion channel 21, respectively. By adopting the volute 10 with the ball table structure, the size of the mixed flow fan can be reduced to the maximum extent, so that the air supply effect of the mixed flow fan is ensured.
The connecting line of the center of the airflow inlet end of the flow guide channel 21 and the center of the air outlet 11 is collinear with the axis of the impeller 30.
The surface of the blade 31 has dimples and/or protrusions. The concave pits and the convex parts can improve airflow, reduce noise and improve air quantity.
According to the utility model discloses an embodiment three discloses a tuber pipe machine, including foretell mixed flow fan. The mixed flow fan is a mixed flow fan between an axial flow mixed flow fan and a centrifugal mixed flow fan, the 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 forms of axial flow and centrifugation, so that the mixed flow fan is called mixed flow. Because the mixed flow fan not only can make the volume little, can guarantee the flow direction and the wind pressure of air current moreover, so install the mixed flow fan in the tuber pipe machine to realize that the wind direction is reversible, change the air-out direction.
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 (14)
1. A mixed flow fan, comprising:
a volute (10);
the current collector (20), the current collector (20) is arranged at the position of an air inlet of the volute (10), the current collector (20) is provided with a flow guide channel (21) communicated with the inside of the volute (10), and the inner diameter of the air flow inlet end of the flow guide channel (21) is D1;
the impeller (30) is arranged inside the volute (10), the maximum diameter of the impeller (30) is D2, and the range of D1/D2 is 0.8-0.9.
2. The mixed flow fan of claim 1,
the flow guide channel (21) is further provided with an air flow outlet end, the inner diameter of the flow guide channel (21) at the air flow outlet end is D3, and the range of D1/D3 is 1.2-1.
3. The mixed flow fan of claim 2,
the distance from the air flow inlet end to the air flow outlet end is H1, and the range of H1/D2 is 0.1-0.3.
4. The mixed flow fan of claim 2,
the flow guide channel (21) 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.
5. The mixed flow fan of claim 4,
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.
6. The mixed flow fan of claim 4,
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.
7. The mixed flow fan of claim 4,
the flow guide channel (21) 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.
8. The mixed flow fan of claim 1,
the impeller (30) comprises blades (31), the maximum height of the blades (31) in the axial direction of the impeller (30) is H2, and the range of H2/D2 is 0.38-0.48.
9. The mixed flow fan of claim 8,
the impeller (30) further comprises a shroud (32), an airflow channel is formed inside the shroud (32), and the blades (31) are positioned in the airflow channel;
the airflow channel is provided with an expansion section, the expansion section is positioned between the air inlet end of the airflow channel and the air outlet end of the airflow channel, and the flow area of the expansion section is gradually increased in the direction from the air inlet end of the airflow channel to the air outlet end of the airflow channel.
10. The mixed flow fan of claim 9,
an air outlet (11) is also arranged on the volute (10);
the distance between the air flow inlet end of the flow guide channel (21) and the air outlet (11) is A, and the ratio range of H2/A is 0.37-0.47.
11. The mixed flow fan of claim 10,
along the radial direction of the impeller (30), the maximum diameter of the volute (10) is B, and the ratio range of B/D2 is 1.1-1.25.
12. The mixed flow fan of claim 10,
the center of the airflow inlet end of the flow guide channel (21) is connected with the center of the air outlet (11) in a line with the axis of the impeller (30).
13. The mixed flow fan of claim 8,
the surface of the blade (31) is provided with pits and/or projections.
14. A ducted air conditioner comprising a mixed flow fan as claimed in any one of claims 1 to 13.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202221287803.6U CN217421629U (en) | 2022-05-27 | 2022-05-27 | Mixed flow fan and ducted air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202221287803.6U CN217421629U (en) | 2022-05-27 | 2022-05-27 | Mixed flow fan and ducted air conditioner |
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| Publication Number | Publication Date |
|---|---|
| CN217421629U true CN217421629U (en) | 2022-09-13 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202221287803.6U Active CN217421629U (en) | 2022-05-27 | 2022-05-27 | Mixed flow fan and ducted air conditioner |
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| Country | Link |
|---|---|
| CN (1) | CN217421629U (en) |
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