CN114688047B - High static pressure centrifugal dust removal fan - Google Patents
High static pressure centrifugal dust removal fan Download PDFInfo
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- CN114688047B CN114688047B CN202210629057.2A CN202210629057A CN114688047B CN 114688047 B CN114688047 B CN 114688047B CN 202210629057 A CN202210629057 A CN 202210629057A CN 114688047 B CN114688047 B CN 114688047B
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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
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
- F04D17/16—Centrifugal pumps for displacing without appreciable compression
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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
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
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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
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/30—Vanes
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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
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
- F04D29/4226—Fan casings
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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
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
- Y02A50/00—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE in human health protection, e.g. against extreme weather
- Y02A50/20—Air quality improvement or preservation, e.g. vehicle emission control or emission reduction by using catalytic converters
- Y02A50/2351—Atmospheric particulate matter [PM], e.g. carbon smoke microparticles, smog, aerosol particles, dust
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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 relates to the technical field of fans, in particular to a high-static pressure centrifugal dust removal fan which comprises a volute and an impeller arranged in the volute, wherein the volute comprises a coaming, and a front plate and a rear plate which are connected to the front side and the rear side of the coaming; the coaming comprises a first diffusion section, a first arc section, a second arc section, a third arc section, a fourth arc section, a volute tongue section and a second diffusion section which are connected in sequence; the distance between the front plate and the rear plate is 170-190, the height of the highest position of the blade is 110-115, and the height of the lowest position of the blade is 78-82; the blades are backward bent, the outermost ends of the air outlet edges of the blades surround the periphery of the blades, and the radial distance between the periphery of the blades and the volute tongue section is 30-34. It has the advantages of high static pressure and good dust collection effect.
Description
Technical Field
The invention relates to the technical field of fans, in particular to a high-static-pressure centrifugal dust removal fan.
Background
In industrial production or daily life, more and more scenes such as post dust removal, laser equipment dust collection, household dust removal and the like are used, and in the dust remover, a centrifugal dust removal fan in the dust remover plays a main role.
When the centrifugal dust removal fan works, the impeller rotates to drive airflow, and the airflow drives dust to enter the dust remover. The performance parameters influencing the dust collection effect of the centrifugal dust removal fan are mainly two, one is volume flow, and the other is static pressure; when the volume flow is large, more air is sucked, namely more dust can be sucked; when the static pressure is high, the suction force is larger, namely larger dust can be sucked. In the centrifugal dust removing fan, it is preferable that the volume flow rate is large and the static pressure is high.
The centrifugal fan generally includes a volute and an impeller disposed in the volute, and when the centrifugal fan is designed, the performance parameters of the centrifugal fan can be changed by changing the structural parameters of the centrifugal fan (for example, changing the structural characteristics and dimensional parameters of the volute and the impeller or adding auxiliary components). In theory, the volume flow is inversely proportional to the static pressure, i.e. for the same shaft power, the higher the volume flow, the lower the static pressure, and the higher the static pressure, the smaller the volume flow. However, in practice, it has been found that the influence of different structural parameters on the performance parameters is not independent, but jointly affects the performance parameters in an organic combination, which makes the volume flow and the static pressure not in a strict linear inverse relationship, i.e. by a reasonable structural arrangement, it is also possible to optimize one of the performance parameters without affecting the other, and a great deal of research and significant results are available in this respect.
However, most of the research is directed to traditional centrifugal fans, such as blowers and ventilators, and mainly to how to increase the volume flow, and the research on centrifugal dust removal fans is little and few. With the continuous improvement of the use requirements of the dust remover, particularly with the expansion of the use scenes, the granularity of impurities to be sucked is larger and larger, high static pressure gradually becomes a performance parameter which is focused on in the dust remover, the static pressure of the centrifugal dust removing fan on the market is generally lower at present, and therefore, a high static pressure centrifugal dust removing fan needs to be designed.
Disclosure of Invention
The invention aims to provide a high-static-pressure centrifugal dust removal fan, and aims to solve the problem that the static pressure of the dust removal fan in the prior art is insufficient.
In order to achieve the purpose, the invention provides a high-static pressure centrifugal dust removal fan which comprises a volute and an impeller arranged in the volute, wherein the volute comprises a coaming, a front plate and a rear plate, the front plate and the rear plate are connected to the front side and the rear side of the coaming, the front plate is provided with an air inlet, the two ends of the coaming, part of the front plate and part of the rear plate jointly enclose an air outlet, the impeller comprises a plurality of blades, a front disc and a rear disc, the front disc and the rear disc are connected to the front side and the rear side of the plurality of blades, and the middle part of the front disc is provided with an air suction inlet; the coaming comprises a first diffusion section, a first arc section, a second arc section, a third arc section, a fourth arc section, a volute tongue section and a second diffusion section which are sequentially connectedA segment; a rectangular coordinate system is established by taking the circle center of the impeller as the origin of coordinates, when the first diffusion section is positioned in the second quadrant and is parallel to the X axis, under the dimensionless counting, the first arc section is tangent with the first diffusion section, and the circle center O of the first arc section 1 Coordinate (-34, 34), radius R 1 Is 409, the central angle 1 is 90-91 degrees, and the center O of the second arc segment 2 Coordinates (29, 29), radius R 2 346, the central angle 2 is 90-91 degrees, and the center O of the third arc segment 3 Coordinates (24, -24), radius R 3 Is 294, the central angle < 3 > is 90-91 degrees, and the center O of the fourth arc segment 4 Coordinates (-21 ), radius R 4 249, and the central angle < 4 > is 31-32 degrees; distance h between front and rear plates 1 Is 170-190, the side of the blade close to the center of the impeller is the inner side, the side of the blade far from the center of the impeller is the outer side, the height of the blade is gradually reduced from the inner side to the outer side, and the height h of the highest position of the blade is 2 110-115, the height h of the lowest part of the blade 3 Is 78 to 82; the blades are backward bent, the outermost ends of the air outlet edges of the blades enclose the periphery of the blades, the radial distance d between the periphery of the blades and the volute tongue section is 30-34, and the number of the blades is 12-16.
Furthermore, a plane perpendicular to the first diffusion section is taken as an air outlet plane, and an included angle between the second diffusion section and the air outlet plane is 60-65 degrees.
Furthermore, the volute tongue section is arc-shaped and has a radius R 5 Is 17-20.
Further, the radius R of the blade outer periphery 6 220-230, the innermost end of the wind inlet side of the plurality of blades is enclosed into the inner periphery of the blade, and the radius R of the inner periphery of the blade 7 105 and 115, the projection of the blade on the rear disk is arc-shaped and has a radius R 8 325-; the inlet angle < 6 > of the blade is 153-158 degrees, and the outlet angle < 7 > of the blade is 44-46 degrees.
Furthermore, the air inlet edge and the air outlet edge of each blade are perpendicular to the rear disc, and the corner far away from the rear disc on the air inlet edge of each blade is set to be radius R 9 Are rounded at 17-18.
Furthermore, the impeller is intercepted by a plane passing through the central axis of the impeller, and the included angle between the front disc and the rear disc on the cross section is 20 degrees.
Furthermore, the air inlet is provided with an air inlet ring, the air inlet ring comprises a connecting part and a necking part, the connecting part is in a circular ring shape and is connected with the front plate, the necking part is connected to the inner periphery of the connecting part and extends into the volute, and the diameter phi of the necking part is gradually reduced from 300 to 252; intercepting the air inlet ring by a plane passing through a central axis of the air inlet ring, wherein an included angle between a connecting part and a necking part on the cross section is 117 degrees; the necking part extends into the air suction port of the front disc.
Further, the radius R of the blade outer periphery 6 220-230, the innermost end of the wind inlet side of the plurality of blades is enclosed into the inner periphery of the blade, and the radius R of the inner periphery of the blade 7 105, the projection of the blade on the rear disk comprises a blade straight-line segment and a blade circular arc segment which are sequentially connected from inside to outside, the blade circular arc segment is tangent with the blade straight-line segment, and the radius R of the blade circular arc segment 10 Radius R of the blade periphery 6 Radius R from the inner periphery of the blade 7 1.4-1.5 times the difference; the inlet angle < 6 > of the blade is 153-158 degrees, and the outlet angle < 7 > of the blade is 44-46 degrees.
Furthermore, one side of the blade close to the center of the impeller is an inner side, one side of the blade far away from the center of the impeller is an outer side, the wind inlet edge of the blade inclines outwards and has an angle of 75-80 degrees relative to the rear disc, and the wind outlet edge of the blade inclines inwards and has an angle of 43-47 degrees relative to the rear disc.
Further, the distance h between the front plate and the rear plate 1 180, height h of the highest part of the blade 2 112, height h of the lowest part of the blade 3 The radial distance d between the periphery of the blade and the volute tongue section is 32, and the number of the blades is 14.
The high static pressure centrifugal dust removal fan provided by the invention improves the structural parameters of the volute and the impeller in a matching way, so that the static pressure is improved and the dust collection performance is improved under the condition of the same shaft power and without influencing the volume flow.
Drawings
FIG. 1 is a partial cross-sectional view of a high static pressure centrifugal dust extraction fan of the present invention;
FIG. 2 is a schematic view of the volute and impeller;
FIG. 3 is a left side view of the volute;
FIG. 4 is a schematic structural view of the shroud;
FIG. 5 is a schematic structural view of the impeller of the first embodiment with a portion of the front disk removed;
FIG. 6 is a side cross-sectional view of the impeller of the first embodiment;
FIG. 7 is a side cross-sectional view of the air scoop ring;
FIG. 8 is a top plan view of the impeller of the second embodiment with the front disk removed;
FIG. 9 is a plan development of the blade of the second embodiment;
FIG. 10 is a graph of performance of a comparative example;
FIG. 11 is a graph of performance of example one;
fig. 12 is a graph of performance for example two.
Description of reference numerals:
1-volute, 11-coaming, 111-first diffusion section, 112-first arc section, 113-second arc section, 114-third arc section, 115-fourth arc section, 116-volute tongue section, 117-second diffusion section, 12-front plate, 121-air inlet, 13-rear plate, 14-air outlet and 141-air outlet plane;
2-impeller, 21-blade, 211-air inlet edge, 212-air outlet edge, 213-blade straight line segment, 214-blade circular arc segment, 22-front disc, 221-air suction inlet and 23-rear disc;
3-air inlet ring, 31-connecting part and 32-necking part.
Detailed Description
The present invention will be described in detail with reference to specific examples.
In the present invention, unless otherwise explicitly specified or limited, when terms such as "disposed on", "connected" or "connected" are present, these terms should be interpreted broadly, and may be, for example, fixedly connected, detachably connected or integrally connected; may be directly connected or connected through one or more intermediaries. The specific meanings of the above-mentioned terms in the present invention can be understood by those skilled in the art according to specific situations. The direction words appearing in the present invention are for better describing the characteristics of the features and the relationships among the features, and it should be understood that when the placing direction of the present invention is changed, the directions of the characteristics of the features and the relationships among the features are correspondingly changed, so the direction words do not constitute an absolute limiting function in the space of the characteristics of the features and the relationships among the features, but only play a relative limiting function.
The structural parameters of the high static pressure centrifugal dust removal fan are explained in a dimensionless mode, namely, the scaling can be carried out in the practical production based on the dimensionless basic structure, and the scaling also falls into the protection scope of the invention.
In the first embodiment, please refer to fig. 1 to 7.
The embodiment provides a high static pressure centrifugal dust removal fan, it includes spiral case 1 and the impeller 2 of setting in spiral case 1, spiral case 1 includes bounding wall 11 and connects front bezel 12 and the back plate 13 in the front and back both sides of bounding wall 11, front bezel 12 is provided with air intake 121, the both ends of bounding wall 11, partial front bezel 12 and partial back plate 13 enclose into air outlet 14 jointly, impeller 2 includes multi-disc blade 21 and connects front bezel 22 and the back plate 23 in the front and back both sides of multi-disc blade 21, the middle part of front bezel 22 is provided with inlet scoop 221. When the dust collector works, the impeller 2 rotates, air passes through the air inlet 121, the air suction opening 221 and the inner cavity of the volute 1 in sequence under the action of the impeller 2 and then is sent out from the air outlet 14, and a dust suction pipe of the dust collector is communicated with the air inlet 121, so that the dust collector can suck air.
In order to optimize the performance of the high static pressure dust-removing fan, in the embodiment, the structure of the enclosing plate 11, the thickness of the inner cavity of the volute 1 (i.e., the distance between the front plate 12 and the rear plate 13), the thickness of the impeller 2 (i.e., the height of the blades 21), the bending mode of the impeller 2 and the radial distance between the impeller 2 and the volute 1 are improved at the same time, and the structural parameters jointly act to improve the performance of the high static pressure dust-removing fan in a mutually matched mode.
In this embodiment, as shown in fig. 4, the shroud plate 11 includes a first diffuser section 111, a first circular arc section 112, a second circular arc section 113, a third circular arc section 114, a fourth circular arc section 115, a volute tongue section 116, and a second diffuser section connected in sequenceA press section 117; a rectangular coordinate system is established by taking the circle center O of the impeller 2 as the origin of coordinates, when the first diffusion section 111 is positioned in the second quadrant and is parallel to the X axis, under the dimensionless counting, the first arc section 112 is tangent to the first diffusion section 111, and the circle center O of the first arc section 112 1 Coordinate (-34, 34), radius R 1 Is 409, the central angle 1 is 90-91 degrees, and the center O of the second arc segment 113 is 2 Coordinates (29, 29), radius R 2 At 346, the central angle 2 is 90-91 degrees, and the center O of the third arc segment 114 3 Coordinates (24, -24), radius R 3 Is 294, the central angle < 3 > is 90-91 degrees, and the center O of the fourth arc segment 115 4 Coordinates (-21 ), radius R 4 249, and the central angle < 4 > is 31-32 degrees.
In the present embodiment, the blades 21 are backward-curved, the outermost ends of the air outlet edges 212 of the plurality of blades 21 enclose a blade periphery, and the radial distance d between the blade periphery and the volute tongue section 116 is 30-34, preferably d is 32.
In the present embodiment, the distance h between the front plate 12 and the rear plate 13 1 Is 170- 1 Is 180. The side of the blade 21 close to the center of the impeller 2 is the inner side, the side of the blade 21 far away from the center of the impeller 2 is the outer side, the height of the blade 21 is gradually reduced from the inner side to the outer side, and the height h of the highest part of the blade 21 is 2 110-115, preferably h 2 And is 112. The height h of the lowest part of the blade 21 3 Is 78-82, preferably h 3 Is 80.
Research finds that the blades of the existing dust removal fan are in a straight plate shape, the blades are not beneficial to generation of wind, airflow is easy to separate at the air outlet edge of the blades, and the existing dust removal fan is low in flow, high in power consumption and low in static pressure. Curved blades can provide higher static pressure than conventional straight blades. Particularly, the backward-bending type arc-shaped blade can further reduce the flow loss of the airflow at the air inlet edge and the air outlet edge of the blade, and the effective flow range and the fan efficiency are improved. Under the condition that the maximum diameter of the volute is fixed, the thickness of the inner cavity of the volute has great influence on various performances of the fan, and the thickness of the inner cavity given by the embodiment is a thickness range with higher static pressure when the volute is used under a centrifugal dust removal fan. Under the condition that the thickness of the inner cavity of the volute is constant, the volume flow and the total pressure can be improved when the height of the blade is increased, but the efficiency and the static pressure of the fan can be reduced; if the height of the blade is reduced, the efficiency and the static pressure of the fan can be improved, but the volume flow and the total pressure can be reduced, and meanwhile, the heights of the air inlet edge and the air outlet edge can simultaneously influence the volume flow, the total pressure, the efficiency and the static pressure of the fan. Through experiments, the given height and gradual change size parameters of the blades 21 in the embodiment can enable the volume flow of the high-static-pressure centrifugal dust removal fan to be basically the same as that of the centrifugal dust removal fan in the prior art, but the static pressure is greatly improved. After the above parameters are selected, the embodiment improves the line shape of the enclosing plate 11 in a matching manner, so that the impact of the airflow on the volute 1 is reduced, and the movement is smoother. The radial distance between the periphery of the blade and the volute tongue section 116 is optimized, because the radial distance between the volute tongue section and the periphery of the blade is increased, the stability of a flow field inside the fan is reduced, but the total pressure and the fan efficiency are improved if the radial distance is reduced, but the noise is increased.
In the present embodiment, a plane perpendicular to the first diffuser section 111 is taken as the air outlet plane 141, and an included angle between the second diffuser section 117 and the air outlet plane 141 is 60-65 degrees, preferably, the included angle is 62 degrees. The volute tongue section 116 is arc-shaped and has a radius R 5 Is 17-20, preferably R 5 Is 18.
In the present embodiment, the radius R of the blade outer periphery 6 Is 220-230, preferably R 6 225, the innermost ends of the wind inlet sides 211 of the plurality of blades 21 enclose a blade inner circumference, the radius R of which 7 105- 7 110, the projection of the blade 21 on the rear disk 23 is arc-shaped and has a radius R 8 325- 8 Is 329.
In the present implementation, the inlet angle < 6 > of the blade 21 is 153-.
In the present embodiment, the wind inlet edge 211 and the wind outlet edge 212 of the blade 21 are both perpendicular to the back plate 23, and the corner of the wind inlet edge 211 of the blade 21 far from the back plate 23 is set to have a radius R 9 Is a rounded corner of 17-18, preferably R 9 Is 18.
In the present embodiment, the impeller 2 is cut out on a plane passing through the central axis of the impeller 2, and the included angle ≤ 8 between the front disc 22 and the rear disc 23 is 20 ° in the cross section.
In this embodiment, the air inlet 121 is provided with an air inlet ring 3, the air inlet ring 3 includes a connecting portion 31 and a throat portion 32, the connecting portion 31 is annular and connected to the front plate 12, the throat portion 32 is connected to the inner periphery of the connecting portion 31 and extends into the scroll casing 1, and the diameter Φ of the throat portion 32 is gradually reduced from 300 to 252; intercepting the air inlet ring 3 by a plane passing through the central axis of the air inlet ring 3, wherein the included angle between the connecting part 31 and the necking part 32 on the cross section is 117 degrees; the throat 32 extends partially into the suction opening 221 of the front plate 22.
In the present embodiment, the number of blades 21 is 12-16, preferably 14.
To verify the present example, a conventional dust exhaust fan model TB150-7.5 was used as a comparative example, and the impeller 2 had a diameter of 450 mm. Meanwhile, based on the preferred structural parameters provided by the first embodiment, the diameter of the impeller 2 is 450mm (namely, the radius R of the blade periphery) 6 225 mm) a high static pressure centrifugal dust removal fan was made as in example one. The comparative example and the first example were subjected to performance tests, and the test results were converted into a medium density of 1.2 kg/m at an atmospheric pressure of 101325Pa, an atmospheric temperature of 20 ℃ and a pressure of 3 Comparative example gave a performance curve as shown in fig. 10, and example one gave a performance curve as shown in fig. 11.
Of these, the comparative examples provide test data for impeller power (i.e., shaft power) in the range of 2.5 to 4.7kW, while the examples provide test data for impeller power in the range of 3.7 to 5.2 kW. The intersection of the impeller powers between 3.7 and 4.7kW (i.e. the portion enclosed by the box in figures 10 and 11) is present in both sets of test data and a comparison of performance can be made within this interval.
As can be seen from the performance curves, for the comparative example,the overall performance trend is that under the condition of improving the power of the impeller, the volume flow is improved, and the full pressure and the static pressure are both reduced; in the course of the impeller power increasing from 3.7kW to 4.7kW, the volume flow is from about 2550m 3 H is increased to about 3800m 3 Full pressure is reduced from about 3500Pa to about 3000Pa, and static pressure is reduced from about 2570Pa to about 800 Pa. For the first embodiment, the overall performance trend is that with increased impeller power, the volumetric flow increases, and both the full pressure and static pressure decrease; in the course of the impeller power increasing from 3.7kW to 4.7kW, the volume flow is from about 2550m 3 H is raised to about 4000m 3 Slightly better than comparative example one, the full pressure decreased from about 3500Pa to about 3000Pa, which is substantially the same as comparative example, but the static pressure decreased from about 3400Pa to about 2800Pa, the absolute value of the static pressure being significantly better than comparative example, and the rate of decrease in the downward trend being also significantly slower than comparative example. In terms of a comparison of performance parameters, the first example has the advantage of a higher static pressure compared to the comparative example, enabling an increase in static pressure without sacrificing volumetric flow.
In addition, for the dust collector, when the static pressure is lower than 1000Pa, the suction force is very small, the practicability is not high, therefore, when the static pressure is lower than 1000Pa, the impeller power is not necessary to be continuously increased, the volume flow rate is only higher, but the static pressure is continuously reduced, the suction force required by dust collection is not provided, and the reason why the subsequent test of the impeller power being more than 4.7kW is not carried out in the performance curve of the comparative example; thus, it can be seen that the comparative examples have a smaller range of performance parameters. As can be seen from the comparison of the performance curves of example one and the comparative example, the separation between the static pressure and the full pressure is much smaller in example one than in the comparative example, and the static pressure drop rate is slower in example one, which makes example one achieve a volume flow rate of about 6800m 3 Static pressure at/h is less than 1000Pa (comparative example only has a volume flow of about 3700m 3 Static pressure at/h is lower than 1000 Pa), therefore, the range of performance parameters of the embodiment is wider, and the use scene is wider.
In conclusion, the fan of the first embodiment has higher efficiency and wider optional working range, and can be used in more use scenes. Meanwhile, based on the optimization of each structural parameter, although the performance parameters are all optimized, the noise is not obviously improved.
In the second embodiment, please refer to fig. 8 and 9.
In this embodiment, the projection structure of the blades 21 on the rear disk 23 is different from that of the first embodiment, but the first embodiment is the same.
In this embodiment, the projection of the blade 21 on the rear disk 23 includes a blade straight-line section 213 and a blade circular arc section 214 connected in sequence from inside to outside, the blade circular arc section 214 is tangent to the blade straight-line section 213, and the radius R of the blade circular arc section 214 10 Radius R of the blade periphery 6 Radius R from the inner periphery of the blade 7 1.4-1.5 times the difference; the inlet angle < 6 of the blade 21 is 153-158 degrees, preferably < 6 is 156 degrees, the outlet angle < 7 of the blade 21 is 44-46 degrees, preferably < 7 is 45 degrees; the side of the blade 21 close to the center of the impeller 2 is the inner side, the side of the blade 21 far away from the center of the impeller 2 is the outer side, the wind inlet edge 211 of the blade 21 inclines outwards and has an angle of 75-80 degrees relative to the rear disc 23, and the wind outlet edge 212 of the blade 21 inclines inwards and has an angle of 43-47 degrees relative to the rear disc 23.
In this embodiment, the projection structure of the blade 21 includes a blade straight line segment 213 and a blade arc segment 214, and the size of the projection structure is matched in a specific range, the structure is different from the structure of a pure straight line segment or a pure arc segment of a conventional blade, and the structure can be seen in a software simulation result, so that the generation of separated flow in a flow channel can be reduced, the generation of wake-jet flow of the impeller is greatly improved, and in cooperation with the inward-inclined arrangement of the air outlet edge 212 of the blade 21, the inclined air outlet edge 212 can suppress jet flow, so that jet flow is more dispersed than that of the conventional impeller, and severe impact between the jet flow and the volute tongue segment 116 is reduced; the structure can achieve the purpose of noise reduction, but correspondingly, performance parameters are reduced due to relative dispersion of jet flows.
To verify the present embodiment, on the basis of the first embodiment, the impeller 2 is replaced by the blade 21 structure provided in the present embodiment, and a high static pressure centrifugal dust removing fan is manufactured as the second embodiment. The second example was tested for performance and the results were converted to 1013 atmosphere25Pa, an atmospheric temperature of 20 ℃ and a medium density of 1.2 kg/m 3 Example two resulted in a performance curve as shown in fig. 12. Comparing the performance curves of the first embodiment shows that the second embodiment is inferior to the first embodiment in terms of volume flow, full pressure, static pressure and fan efficiency, but is obviously superior to the comparative example, and the second embodiment is 5-10dB lower in A sound level than the first embodiment, which is suitable for use in a use scene with higher requirements on noise, such as a household dust collector.
In conclusion, the high static pressure centrifugal dust removal fan provided by the invention has higher static pressure and good dust collection performance.
The features of the embodiments and embodiments described above may be combined with each other without conflict.
Finally, it should be noted that the above embodiments are only used for illustrating the technical solutions of the present invention, and not for limiting the protection scope of the present invention, although the present invention is described in detail with reference to the preferred embodiments, it should be understood by those skilled in the art that modifications or equivalent substitutions can be made on the technical solutions of the present invention without departing from the spirit and scope of the technical solutions of the present invention.
Claims (10)
1. The utility model provides a high static pressure centrifugation dust exhausting fan, includes the spiral case and sets up the impeller in the spiral case, and the spiral case includes the bounding wall and connects front bezel and the back plate in the front and back both sides of bounding wall, and the front bezel is provided with the air intake, and the both ends of bounding wall, partial front bezel and partial back plate enclose into the air outlet jointly, and the impeller includes multi-disc blade and connects front bezel and the back plate in both sides around the multi-disc blade, and the middle part of front bezel is provided with inlet scoop, its characterized in that:
the coaming comprises a first diffusion section, a first arc section, a second arc section, a third arc section, a fourth arc section, a volute tongue section and a second diffusion section which are connected in sequence; a rectangular coordinate system is established by taking the circle center of the impeller as a coordinate origin O, when the first diffusion section is positioned in the second quadrant and is parallel to the X axis, the first arc section is tangent to the first diffusion section under the dimensionless counting, and the circle center O of the first arc section 1 Coordinate (-34, 34), radius R 1 Is 409, the central angle < 1 > is 90-91 degrees, and the second step isCircle center O of arc segment 2 Coordinates (29, 29), radius R 2 346, the central angle 2 is 90-91 degrees, and the center O of the third arc segment 3 Coordinates (24, -24), radius R 3 Is 294, the central angle < 3 > is 90-91 degrees, and the center O of the fourth arc segment 4 Coordinates (-21 ), radius R 4 249, and the central angle < 4 > is 31-32 degrees;
distance h between front and rear plates 1 170-190, the side of the blade close to the center of the impeller is the inner side, the side of the blade far from the center of the impeller is the outer side, the height of the blade is gradually reduced from the inner side to the outer side, and the height h of the highest position of the blade is 2 110-115, the height h of the lowest part of the blade 3 Is 78 to 82;
the blades are backward bent, the outermost ends of the air outlet edges of the blades surround the periphery of the blades, the radial distance d between the periphery of the blades and the volute tongue section is 30-34, and the number of the blades is 12-16.
2. The high static pressure centrifugal dust removal fan of claim 1, wherein: and taking a plane perpendicular to the first diffusion section as an air outlet plane, wherein an included angle between the second diffusion section and the air outlet plane is 60-65 degrees.
3. The high static pressure centrifugal dust removal fan of claim 1, wherein: the volute tongue section is arc-shaped and has a radius R 5 Is 17-20.
4. The high static pressure centrifugal dust removal fan of claim 1, wherein: radius R of blade periphery 6 220-230, the innermost end of the wind inlet side of the plurality of blades is enclosed into the inner periphery of the blade, and the radius R of the inner periphery of the blade 7 105 and 115, the projection of the blade on the rear disk is arc-shaped and has a radius R 8 325-;
the inlet angle < 6 > of the blade is 153-158 degrees, and the outlet angle < 7 > of the blade is 44-46 degrees.
5. The high static pressure centrifugal dust removal fan of claim 4, wherein: inlet and outlet edges of bladesThe wind edges are all vertical to the back disk, and the corners of the wind edges of the blades far away from the back disk are set to be radius R 9 Are rounded at 17-18.
6. The high static pressure centrifugal dust removal fan of claim 1, wherein: the impeller is intercepted by a plane passing through the central axis of the impeller, and the included angle between a front disc and a rear disc on the cross section is 20 degrees.
7. The high static pressure centrifugal dust removal fan of claim 6, wherein: the air inlet is provided with an air inlet ring, the air inlet ring comprises a connecting part and a necking part, the connecting part is in a circular ring shape and is connected with the front plate, the necking part is connected to the inner periphery of the connecting part and extends into the volute, and the diameter phi of the necking part is gradually reduced from 300 to 252;
intercepting the air inlet ring by a plane passing through a central axis of the air inlet ring, wherein an included angle between a connecting part and a necking part on the cross section is 117 degrees;
the necking part extends into the air suction port of the front disc.
8. The high static pressure centrifugal dust removal fan of claim 1, wherein: radius R of blade periphery 6 220-230, the innermost end of the wind inlet side of the plurality of blades is enclosed into the inner periphery of the blade, and the radius R of the inner periphery of the blade 7 105, the projection of the blade on the rear disk comprises a blade straight-line segment and a blade circular arc segment which are sequentially connected from inside to outside, the blade circular arc segment is tangent with the blade straight-line segment, and the radius R of the blade circular arc segment 10 Radius R of the blade periphery 6 Radius R from the inner periphery of the blade 7 1.4-1.5 times the difference;
the inlet angle < 6 > of the blade is 153-158 degrees, and the outlet angle < 7 > of the blade is 44-46 degrees.
9. The high static pressure centrifugal dust removal fan of claim 8, wherein: the side of the blade close to the center of the impeller is the inner side, the side of the blade far away from the center of the impeller is the outer side, the wind inlet edge of the blade inclines outwards and is 75-80 degrees relative to the angle of the rear disc, and the wind outlet edge of the blade inclines inwards and is 43-47 degrees relative to the angle of the rear disc 12.
10. The high static pressure centrifugal dust removal fan according to any one of claims 1 to 9, wherein: distance h between front and rear plates 1 180, height h of the highest part of the blade 2 112, height h of the lowest part of the blade 3 The radial distance d between the periphery of the blade and the volute tongue section is 32, and the number of the blades is 14.
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| CN202210629057.2A CN114688047B (en) | 2022-06-06 | 2022-06-06 | High static pressure centrifugal dust removal fan |
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| CN114688047B true CN114688047B (en) | 2022-09-02 |
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| CN117167295B (en) * | 2023-11-03 | 2024-01-02 | 佛山市南海九洲普惠风机有限公司 | High static pressure backward multi-wing centrifugal fan |
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| JP4952006B2 (en) * | 2006-03-07 | 2012-06-13 | 株式会社デンソー | Centrifugal blower |
| CN105041722B (en) * | 2015-08-26 | 2017-08-29 | 宁波方太厨具有限公司 | A kind of centrifugal blower volute |
| CN209458150U (en) * | 2018-01-26 | 2019-10-01 | 东莞市华通通风除尘设备有限公司 | A kind of low noise efficient rate dedusting special fan |
| CN109973433B (en) * | 2019-02-27 | 2020-01-21 | 华中科技大学 | Volute with concave inclined volute tongue structure |
| CN111878424B (en) * | 2020-08-25 | 2024-05-17 | 中山市高途五金制品有限公司 | Large air volume volute fan |
| CN113187749B (en) * | 2021-05-31 | 2023-07-25 | 佛山市南海九洲普惠风机有限公司 | High-efficient air conditioner fan |
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