CN114810671B - Special high-speed centrifugal fan of small-size dust remover - Google Patents
Special high-speed centrifugal fan of small-size dust remover Download PDFInfo
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- CN114810671B CN114810671B CN202210732213.8A CN202210732213A CN114810671B CN 114810671 B CN114810671 B CN 114810671B CN 202210732213 A CN202210732213 A CN 202210732213A CN 114810671 B CN114810671 B CN 114810671B
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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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- B—PERFORMING OPERATIONS; TRANSPORTING
- B08—CLEANING
- B08B—CLEANING IN GENERAL; PREVENTION OF FOULING IN GENERAL
- B08B5/00—Cleaning by methods involving the use of air flow or gas flow
- B08B5/04—Cleaning by suction, with or without auxiliary action
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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
- F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
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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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- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention relates to the technical field of centrifugal fans, in particular to a special high-speed centrifugal fan for a small dust remover, which comprises a volute and an impeller arranged in the volute; the impeller comprises a plurality of blades arranged in the circumference, the diameter of the outer circumference formed by the outermost ends of the blades is smaller than 300mm, the blades comprise a long blade and a short blade which are arranged in the circumference at intervals, the long blade and the short blade are both in a backward bending mode, the outermost ends of the long blade and the short blade are both positioned on the same outer circumference, and the diameter phi of the outer circumference is 1 Are all 223; distance h between front and rear plates 1 Is phi 1 0.3-0.31 times of the height of the blade relative to the rear disc, h 2 Is phi 1 0.16-0.17 times of; the radial distance e between the peripheral circle and the volute tongue section is 5-7, and the radius R of the volute tongue section 5 Is 0.8-1.2 times of e. The special high-speed centrifugal fan for the small dust remover has the advantages of higher fan efficiency, larger effective flow, good dust absorption performance and less energy consumption.
Description
Technical Field
The invention relates to the technical field of centrifugal fans, in particular to a high-speed centrifugal fan special for a small dust remover.
Background
In industrial production, more and more scenes are used for dust collectors, such as post dust collection, laser equipment dust collection and the like, and in the dust collectors, a centrifugal fan in the dust collectors plays a main role.
When the centrifugal fan works, the impeller rotates to drive airflow, and the airflow drives dust to enter the dust remover. Fan efficiency is an important performance parameter of a centrifugal fan and is calculated by the formula of volumetric flow rate, full pressure, and shaft power (i.e., impeller power). When the volume flow (expressed as flow velocity under the air suction port with the same size) is large, more air is sucked, and more dust can be sucked; when the pressure is high, the suction force is larger, and larger dust can be sucked; the higher the fan efficiency, i.e. the lower the energy consumption level, the more power saving. In the centrifugal fan, the volume flow and the total pressure are in an inverse relation, along with the continuous improvement of the power of the impeller, the volume flow is continuously increased, but the total pressure is continuously reduced, the inverse relation enables a fan efficiency curve of the centrifugal fan to be a curve which is ascending firstly and then descending, and a fan efficiency maximum value exists.
With the increasing use scenes of the dust remover, the performance requirement of the dust remover is higher and higher. In particular, the modern industry is constantly pursuing miniaturization and weight reduction of equipment, as is the current demand for dust collectors in industrial production. For example, set up the dust remover on every staff's station side or laser equipment, its specification can not design too big, otherwise can occupy more space, and likewise, the centrifugal fan in the dust remover also need do for a short time correspondingly, but, when the specification of centrifugal fan is accomplished to be less than certain extent, if when the impeller diameter is less than 300mm, reduce traditional centrifugal fan equal scale to required size after, each performance parameter of centrifugal fan all can descend by a wide margin, and traditional centrifugal fan structure can't be suitable for. Therefore, in the prior art, a special centrifugal fan is designed for a small dust collector, and the performance parameters of the centrifugal fan can be changed by changing the structural parameters of the centrifugal fan (such as changing the structural characteristics and the dimensional parameters of a volute and an impeller or adding an auxiliary component).
The fan efficiency of the centrifugal fan with the impeller diameter smaller than 300mm on the market can only reach 73% at most, the fan efficiency of the level means that more electric energy is wasted, the current trend of energy conservation and emission reduction cannot be met, and the use cost of a dust remover user is increased.
Disclosure of Invention
The invention aims to provide a special high-speed centrifugal fan for a small dust remover, and aims to solve the problem of low fan efficiency of a centrifugal fan with an impeller diameter smaller than 300mm in the prior art.
In order to achieve the purpose, the invention provides a special high-speed centrifugal fan for a small dust remover, 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, two ends of the coaming, part of the front plate and part of the rear plate jointly enclose an air outlet, and the impeller comprises a plurality of blades arranged around the periphery and a plurality of blades connected with the bladesThe front disc and the rear disc are connected to the front side and the rear side of the plurality of blades, an air suction opening is formed in the middle of the front disc, one end, far away from the circle center O of the impeller, of each blade is an outer end, one end, close to the circle center O of the impeller, of each blade is an inner end, the diameter of a peripheral circle formed by the outermost ends of the plurality of blades is smaller than 300mm, and the enclosing plate 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 connected; under dimensionless counting, a rectangular coordinate system is established by taking the circle center O 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, the first arc section is tangent to the first diffusion section, and the circle center O of the first arc section is tangent to the first diffusion section 1 Coordinate is (-6, 2), radius R 1 154, the central angle 1 is 88 to 89 degrees, and the center O of the second arc segment 2 Coordinate (7, 7), radius R 2 Is 140 degrees, the central angle 2 is 90-91 degrees, and the center O of the third arc segment 3 Coordinates (6, -7), radius R 3 127, the central angle 3 is 90-91 degrees, and the center O of the fourth arc segment 4 Coordinates (-6, -6), radius R 4 114, the central angle 4 is 32-34 degrees, the volute tongue section is arc-shaped, and two ends of the volute tongue section are respectively tangent with the fourth arc section and the second diffusion section; the multiple blades comprise long blades and short blades which are arranged at intervals on the periphery, the long blades and the short blades are backward bent, the outermost ends of the long blades and the outermost ends of the short blades are located on the same peripheral circle, and the diameter phi of the peripheral circle 1 Are all 223; distance h between front and rear plates 1 Is phi 1 0.3-0.31 times of the height of the blade relative to the rear disc, h 2 Is phi 1 0.16-0.17 times of; the radial distance e between the peripheral circle and the volute tongue section is 5-7, and the radius R of the volute tongue section 5 Is 0.8-1.2 times of e.
Further, the diameter phi of the inner circumference surrounded by the innermost ends of the long blades 2 80-85, the diameter phi of the inner circumference surrounded by the innermost ends of the short blades 3 148 and 152.
Furthermore, the projection of the long blade on the rear disk is arc-shaped and the radius R of the long blade 6 Is phi 1 And phi 2 0.5-0.6 times the difference; the inlet angle 6 of the long blade is 110 degrees and 120 degrees, and the outlet of the long bladeThe wind angle 7 is 40-43 degrees.
Furthermore, the projection of the short blade on the rear disk is arc-shaped and the radius R of the short blade is 7 Is phi 1 And phi 3 1-1.1 times the difference; the inlet wind angle of the short blades is 8-10 degrees greater than that of 6, and the outlet wind angle of the short blades is equal to 7.
Furthermore, the wind inlet edge of the long blade is inclined relative to the rear disc, the inclination angle & lt 5 & gt is 78-82 degrees, the connection point of the wind inlet edge of the long blade and the rear disc is closer to the center of the impeller relative to the connection point of the long blade and the front disc, and the wind outlet edge of the long blade is perpendicular relative to the rear disc.
Further, the air inlet edge of the short blade is vertical to the rear disc, and the air outlet edge of the short blade is vertical to the rear disc.
Further, the number of the long blades and the short blades is 12.
Furthermore, one side of each blade close to the circle center of the impeller is the inner side, one side of each blade far away from the circle center of the impeller is the outer side, the height of each blade relative to the rear disc is gradually reduced from inside to outside, and the lowest value h of each blade relative to the height of the rear disc is 3 Is phi 1 0.1-0.11 times of the total weight of the powder.
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 73-78 degrees.
Furthermore, the air inlet is provided with a necking part extending into the volute, and the diameter phi of the necking part 4 Gradually decreases from 100 to 86, and the depth h of the necking part extending into the volute 4 Is 22; the necking part extends into the air suction port of the front disc.
The high-speed centrifugal fan special for the small dust collector improves the fan efficiency by 10-15 percent, improves the dust collection performance and reduces the energy consumption by matching and improving the structural parameters of the volute and the impeller.
Drawings
FIG. 1 is a partial sectional view of a high-speed centrifugal fan for a compact dust collector of the present invention;
FIG. 2 is a schematic view of the volute and impeller configuration;
FIG. 3 is a schematic line drawing of the shroud;
FIG. 4 is a schematic structural view of an impeller;
FIG. 5 is a side cross-sectional view of the impeller;
FIG. 6 is a side cross-sectional view of a volute;
FIG. 7 is a graph of performance of a comparative example;
fig. 8 is a graph of performance of the test example.
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-long blade, 211-wind inlet edge of long blade, 212-wind outlet edge of long blade, 22-short blade, 221-wind inlet edge of short blade, 222-wind outlet edge of short blade, 23-front disc, 231-wind inlet, 24-rear disc;
3-a choke portion.
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 invention adopts a dimensionless mode to explain the structural parameters of the high-speed centrifugal fan special for the small dust remover, namely, the dimensionless basic structure can be subjected to scaling in the actual production, and the scaling also falls into the protection scope of the invention. However, since the high-speed centrifugal fan for a small-sized dust collector is suitable for a small-sized dust collector, the enlargement range should be such that the diameter of the impeller 2 (i.e., the diameter of the outer circumference surrounded by the outermost ends of the plurality of blades) is less than 300 mm.
The embodiment provides a special high-speed centrifugal fan for a small dust collector, as shown in fig. 1 to 6, the special high-speed centrifugal fan comprises a volute 1 and an impeller 2 arranged in the volute 1, the volute 1 comprises a coaming 11, and a front plate 12 and a rear plate 13 which are connected to the front side and the rear side of the coaming 11, the front plate 12 is provided with an air inlet 121, two ends of the coaming 11, a part of the front plate 12 and a part of the rear plate 13 jointly enclose an air outlet 14, the impeller 2 comprises a plurality of blades arranged around the periphery, and a front disc 23 and a rear disc 24 which are connected to the front side and the rear side of the plurality of blades, and the middle part of the front disc 23 is provided with an air suction inlet 231. During work, the impeller 2 rotates, and air passes through the air inlet 121, the air suction opening 231 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.
In order to optimize the performance of the high-speed centrifugal fan special for the small dust collector, the structure of the enclosing plate 11, the thickness of the inner cavity of the volute 1 (namely, the distance between the front plate 12 and the rear plate 13), the thickness of the impeller 2 (namely, the height of the blades relative to the rear disc 24), the form and the shape of the impeller 2 and the radial distance between the outer circumference and the volute tongue section 116 are improved simultaneously, and the structural parameters cooperate with each other to improve the performance parameters of the high-speed centrifugal fan special for the small dust collector.
In this embodiment, as shown in fig. 3, the shroud 11 includes a first diffuser section 111, a first arc section 112, a second arc section 113, a third arc section 114, a fourth arc section 115, a volute tongue section 116, and a second diffuser section 117 that are connected in sequence, a rectangular coordinate system is established with a center O of the impeller 2 as an origin of coordinates, when the first diffuser section 111 is located in the second quadrant and is parallel to the X axis, the first arc section 112 is tangent to the first diffuser section 111, the center O of the first arc section 112 is parallel to the X axis 1 Coordinate is (-6, 2), radius R 1 154, central angleThe angle 1 is 88-89 degrees, and the center O of the second arc segment 113 2 Coordinate (7, 7), radius R 2 Is 140 degrees, the central angle 2 is 90-91 degrees, and the center O of the third arc segment 114 3 Coordinates (6, -7), radius R 3 127, the central angle 3 is 90-91 degrees, and the center O of the fourth arc segment 115 4 Coordinates (-6, -6), radius R 4 Is 114, the central angle 4 is 32-34 degrees, the volute tongue section 116 is arc-shaped, and the two ends of the volute tongue section are respectively tangent with the fourth arc section 115 and the second diffuser section 117. The plane perpendicular to the first diffusion section 111 is taken as an air outlet plane 141, the included angle between the second diffusion section 117 and the air outlet plane 141 is 73-78 degrees, and preferably, the included angle 10 is 75 degrees.
As shown in fig. 4 and 5, in this embodiment, one end of each blade far from the center O of the impeller is an outer end, one end of each blade near the center O of the impeller is an inner end, the plurality of blades include long blades 21 and short blades 22 circumferentially and alternately arranged, the long blades 21 and the short blades 22 are backward-curved, the outermost ends of the long blades 21 and the outermost ends of the short blades 22 are located on the same peripheral circle, and the diameter Φ of the peripheral circle is the same as the diameter Φ of the long blade 21 and the short blade 22 1 Are all 223.
In the present embodiment, as shown in fig. 5 and 6, the distance h between the front plate 12 and the rear plate 13 1 Is phi 1 0.3-0.31 times of (A), preferably h 1 67, maximum height h of the blade relative to the rear disc 24 2 Is phi 1 0.16-0.17 times of (A), preferably h 2 Is 36. The side of the blade close to the center of the impeller 2 is the inner side, the side of the blade far away from the center of the impeller 2 is the outer side, the height of the blade relative to the back disk 24 is gradually reduced from the inside to the outside, and the lowest value h of the height of the blade relative to the back disk 3 Is phi 1 0.1 to 0.11 times of (A), preferably h 3 Is 23.
In the present embodiment, as shown in fig. 2, the radial distance e between the outer circumference circle and the volute tongue section 116 is 5-7, preferably, e is 6; radius R of volute tongue section 116 5 Preferably 0.8 to 1.2 times e, R 5 Is 6.
In the present embodiment, the number of the long blades 21 and the short blades 22 is 12 each.
The special high-speed centrifugal fan for the small dust collector adopts irregular coordinate points as the circle centers of four arc sections, and is matched with a specific arc radius and a specific circle center angle to determine a new shape line of the volute 1 and inhibit total pressure loss; by designing the radial distance between the outer circumference circle and the volute tongue section 116 and the radius of the volute tongue section 116 in a matching manner, the vortex of the air outlet 14 and the airflow disturbance in the volute casing 1 can be inhibited, and the diameter of the outer circumference circle of the impeller 2 is basically determined; the inner cavity thickness (namely the distance between the front plate 12 and the rear plate 13), the thickness of the impeller 2 (namely the height of the blades relative to the rear disc 24) and the blade form of the volute 1 are redesigned by combining the size parameters of the impeller 2; the above factors interact to improve volumetric flow, total pressure and fan efficiency.
In the present embodiment, as shown in fig. 4 and 5, the inner circumference diameter Φ surrounded by the innermost ends of the plurality of long blades 21 2 Is 80-85, preferred phi 2 Is 81; inner circumference diameter phi surrounded by innermost ends of the plurality of short blades 22 3 Is 148- 3 Is 149. The projection of the long blade 21 on the rear disk 24 is arc-shaped and has a radius R 6 Is phi 1 And phi 2 0.5 to 0.6 times the difference, preferably R 6 Is 78; the inlet angle < 6 of the long blade 21 is 110 < 120 >, the preferable < 6 > is 114 degrees, the outlet angle < 7 of the long blade 21 is 40-43 degrees, and the preferable < 7 > is 41 degrees. The projection of the short blades 22 on the rear disk 24 is arc-shaped and has a radius R 7 Is phi 1 And phi 3 1-1.1 times the difference, preferably R 7 Is 78; the inlet angle of the short blades 22 is 8-10 degrees greater than 6, the preferable angle 8 is 124 degrees, the outlet angle of the short blades 22 is equal to 7, and the preferable angle 9 is 41 degrees.
In the embodiment, the wind inlet edge 211 of the long blade is inclined relative to the rear disc 24, the inclination angle & lt 5 is 78-82 degrees, preferably & lt 5 & gt is 80 degrees, the connection point of the wind inlet edge 211 of the long blade and the rear disc 24 is closer to the center of the impeller 2 relative to the connection point of the wind inlet edge 211 of the long blade and the front disc 23, and the wind outlet edge 212 of the long blade is vertical to the rear disc 24. The inlet edge 221 of the short blade is perpendicular to the rear disk 24, and the outlet edge 222 of the short blade is perpendicular to the rear disk 24.
In the present embodiment, as shown in fig. 6, the air inlet 121 is provided to the volute1 an inwardly extending throat 3, the diameter phi of the throat 3 4 Gradually decreases from 100 to 86, and the depth h of the necking part 3 extending into the volute 1 4 Is 22; the throat portion 3 partially extends into the air suction opening 231 of the front plate 23. The shape and size of the air inlet 121 relate to the air inlet effect of the whole fan, so that the air flow smoothly enters the impeller 2. Increasing the volume flow of the inlet 121 increases the volume flow but decreases the static pressure (and decreases the total pressure), and conversely, decreasing the volume flow but increasing the total pressure, the size and shape of the inlet 121 is the preferred configuration to achieve higher fan efficiency.
To verify the present example, a conventional DC brushless centrifugal fan model WEM-80 was used as a comparative example, with an impeller diameter of 223 mm. Meanwhile, based on the preferable structural parameters provided by the embodiment, a high-speed centrifugal fan special for a small dust collector is prepared with the diameter of the impeller 2 (that is, the diameter of the outer circumference surrounded by the outermost ends of the plurality of blades) being 223mm, and is taken as a test example. The comparative example and the test 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 Test data under test conditions, comparative examples gave test data as shown in table 1 and performance curves as shown in fig. 7, and test examples gave test data as shown in table 2 and performance curves as shown in fig. 8.
TABLE 1
TABLE 2
From the test data and the performance curve, it can be seen that, for the comparative example, the overall performance trend is that, under the condition of the increased impeller power, the volume flow is increased, the full pressure and the static pressure are both decreased, the fan efficiency is increased first and then decreased, and the highest point of the fan efficiency is 73%. For the test 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; the fan efficiency also rises first and then falls, but the highest point of the fan efficiency is 88%. In terms of a performance curve comparison, the fan efficiency of the test case is generally 10-15 percentage points higher than the fan efficiency of the comparative example under the same impeller power (i.e., shaft power). Further, in terms of a comparison of the performance curves, in the comparative example, the volume flow rate was only about 900Pa when the static pressure was close to 0, whereas in the test example, the volume flow rate was about 1050Pa when the static pressure was close to 0, and therefore, the effective volume flow rate of the test example was improved by 10 percentage points or more and the flow rate of the test example was larger.
In conclusion, the special high-speed centrifugal fan for the small dust remover has higher fan efficiency and larger effective flow, can improve the dust collection performance and reduce the energy consumption.
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 special high-speed centrifugal fan of small-size dust remover, including spiral case and the impeller of setting in the spiral case, 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, the front bezel is provided with the air intake, the both ends of bounding wall, part front bezel and part back plate enclose into the air outlet jointly, the impeller includes the multi-disc blade that the ring week set up and connects front bezel and the back plate in both sides around the multi-disc blade, the middle part of front bezel is provided with the inlet scoop, the one end of keeping away from the centre of a circle O of impeller on the blade is the outer end, the one end that is close to centre of a circle O of impeller is inner on the blade, the periphery diameter that the outermost end of multi-disc blade encloses is less than 300mm, the bounding wall is including the first diffusion section that connects gradually, first circular arc section, second circular arc section, third circular arc section, fourth circular arc section, volute tongue section and second diffusion section, a serial communication port, its characterized in that:
under dimensionless counting, a rectangular coordinate system is established by taking the circle center O 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, the first arc section is tangent to the first diffusion section, and the circle center O of the first arc section is tangent to the first diffusion section 1 Coordinate is (-6, 2), radius R 1 154, the central angle 1 is 88 to 89 degrees, and the center O of the second arc segment 2 Coordinate (7, 7), radius R 2 Is 140 degrees, the central angle 2 is 90-91 degrees, and the center O of the third arc segment 3 Coordinates (6, -7), radius R 3 127, the central angle 3 is 90-91 degrees, and the center O of the fourth arc segment 4 Coordinates (-6, -6), radius R 4 114, the central angle 4 is 32-34 degrees, the volute tongue section is arc-shaped, and two ends of the volute tongue section are respectively tangent with the fourth arc section and the second diffusion section;
the multiple blades comprise long blades and short blades which are arranged at intervals on the periphery, the long blades and the short blades are backward bent, the outermost ends of the long blades and the outermost ends of the short blades are located on the same peripheral circle, and the diameter phi of the peripheral circle 1 Is 223;
distance h between front and rear plates 1 Is phi 1 0.3-0.31 times of the height of the blade relative to the rear disc, h 2 Is phi 1 0.16-0.17 times of;
the radial distance e between the peripheral circle and the volute tongue section is 5-7, and the radius R of the volute tongue section 5 Is 0.8-1.2 times of e.
2. The high-speed centrifugal fan special for the small dust collector as claimed in claim 1, wherein: the diameter phi of the inner circle surrounded by the innermost ends of the long blades 2 80-85, the diameter phi of the inner circumference formed by the innermost ends of the short blades 3 148 and 152.
3. The high-speed centrifugal fan special for the small dust collector as claimed in claim 2, wherein: the projection of the long blade on the rear disk is arc-shaped and the radius R of the long blade 6 Is phi 1 And phi 2 The difference is 0.5-0.6 times of the total weight; the wind inlet angle < 6 > of the long blade is 110-120 degrees, and the wind outlet angle < 7 > of the long blade is 40-43 degrees.
4. The high-speed centrifugal fan special for the small dust collector as claimed in claim 3, wherein: the projection of the short blade on the rear disk is arc-shaped and the radius R of the short blade 7 Is phi 1 And phi 3 1-1.1 times the difference; the inlet wind angle of the short blades is 8-10 degrees greater than that of 6, and the outlet wind angle of the short blades is equal to 7.
5. The high-speed centrifugal fan special for the small dust collector as claimed in claim 1, wherein: the air inlet edge of the long blade is inclined relative to the rear disc, the inclination angle is 78-82 degrees, the connection point of the air inlet edge of the long blade and the rear disc is closer to the center of the impeller relative to the connection point of the air inlet edge of the long blade and the front disc, and the air outlet edge of the long blade is vertical relative to the rear disc.
6. The high-speed centrifugal fan special for the small dust collector as claimed in claim 5, wherein: the air inlet edge of the short blade is vertical to the rear disc, and the air outlet edge of the short blade is vertical to the rear disc.
7. The high-speed centrifugal fan special for the small dust collector as claimed in claim 1, wherein: the number of the long blades and the short blades is 12.
8. The high-speed centrifugal fan special for the small dust collector as claimed in claim 1, 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 height of the blade relative to the rear disc is gradually reduced from inside to outside, and the lowest value h of the height of the blade relative to the rear disc is 3 Is phi 1 0.1-0.11 times of the total weight of the powder.
9. The high-speed centrifugal fan special for the small dust collector as claimed in 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 73-78 degrees.
10. The high-speed centrifugal fan special for the small dust collector as claimed in claim 1, wherein: the air inlet is provided with a necking part extending into the volute, and the diameter phi of the necking part 4 Gradually decreases from 100 to 86, and the depth h of the necking part extending into the volute 4 Is 22;
the necking part extends into the air suction port of the front disc.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202210732213.8A CN114810671B (en) | 2022-06-27 | 2022-06-27 | Special high-speed centrifugal fan of small-size dust remover |
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| CN202210732213.8A CN114810671B (en) | 2022-06-27 | 2022-06-27 | Special high-speed centrifugal fan of small-size dust remover |
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| CN114810671B true CN114810671B (en) | 2022-09-16 |
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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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| Publication number | Priority date | Publication date | Assignee | Title |
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| GB530149A (en) * | 1939-06-19 | 1940-12-05 | Howden James & Co Ltd | Improvements in or relating to fans incorporating dust collectors |
| CN104131998B (en) * | 2014-07-23 | 2016-08-31 | 中联重科股份有限公司 | Fan and sweeping machine |
| CN204140461U (en) * | 2014-08-09 | 2015-02-04 | 长沙华中一鼓风机有限公司 | Novel material conveying centrifugal blower |
| CN211397988U (en) * | 2019-12-19 | 2020-09-01 | 湖南联诚轨道装备有限公司 | Asymmetric centrifugal impeller fan |
| CN214742211U (en) * | 2021-03-26 | 2021-11-16 | 浙江尔格科技股份有限公司 | High-flow high-efficiency centrifugal 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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