CN111927823A - Centrifugal impeller and high-specific-speed energy-saving centrifugal dust removal fan - Google Patents

Abstract

The invention discloses a centrifugal impeller and a high specific speed energy-saving centrifugal dust removal fan, wherein a centrifugal impeller comprises: a hub for installing a rotating shaft; at least one group of blade assemblies is arranged on the hub, and each group of blade assemblies includes several The blades are circumferentially arranged around the hub; along the direction from the blade head to the blade tail, the blades include arc segments and straight segments, and the straight segments are inclined radially relative to the hub; the directions of inclination of each blade are consistent. The blades of the centrifugal impeller are combined blades of arc segments and straight segments, which can effectively improve the flow of airflow, avoid airflow loss, obtain larger airflow and meet the requirements of low noise. Therefore, the high specific speed and energy-saving centrifugal dust removal fan with the centrifugal impeller can greatly reduce the volume of the whole equipment while increasing the specific speed, reduce the structural cost, effectively improve the airflow delivered by the fan, and fill the national standard centrifugal fan. Blank in the spectrum of medium to large flow, medium pressure type.

Description

A centrifugal impeller and high specific speed energy-saving centrifugal dust removal fan

technical field

The invention belongs to the technical field of impellers, and in particular relates to a centrifugal impeller and a high-specific rotational speed energy-saving centrifugal dust-removing fan.

Background technique

At present, the large-scale dust removal fans used in industrial dust removal fan systems are basically concentrated in the 4-73 series with a specific speed of 73, the 4-60 series with a specific speed of 60, and the 5-48 and 6-48 series with a specific speed of 48. scope. With the deepening of ultra-clean emission, the number of filter bins increases, the filter area increases, and the filter air speed further decreases from the original 1m/min to 0.7-0.8m/min, and the dust removal system requires a larger air volume than the original. The pressure of the system will be reduced. Under the premise that the design speed of the fan remains unchanged, the specific speed of the fan model will be further increased, and the basic range is between 85 and 90. In this way, if the 4-73 or 4-60 series is still used, the operating point of the fan is bound to be in the large flow area, the impact loss will increase, and the operating efficiency will deviate from the optimal design point. The resistance tends to increase gradually, and the 4-73 or 4-60 series fans used will not be able to meet the higher requirements of ultra-clean emission on dust removal air volume.

If the method of reducing the design speed of the first gear fan is used for design and selection, and the existing 4-73 and 4-60 series fans are used, the external dimensions will increase by more than 25%, which not only occupies a large space, but also increases the equipment cost significantly. Construction costs will also increase at the same time.

Customers have high requirements on the overall performance of the fan and the cost should be as low as possible. Facing the increasingly competitive fan market, it is necessary to develop fan products that meet individual requirements. Aiming at the fan series type spectrum of the existing national standard products, aiming at high efficiency, energy saving and low noise, fill the blank area in the type spectrum, and develop a high specific speed energy-saving centrifugal dust removal fan product.

SUMMARY OF THE INVENTION

In order to solve the technical problems raised in the background art, the present invention provides a centrifugal impeller and a high-specific rotational speed energy-saving centrifugal dust-removing fan.

The technical scheme of the present invention is:

A centrifugal impeller, comprising: a hub for installing a rotating shaft; at least one group of blade assemblies is arranged on the hub, and each group of the blade assemblies includes a plurality of blades circumferentially arranged along the hub; along the blades From the blade head to the blade tail, the blade includes an arc-shaped segment and a straight segment, and the straight segment is radially inclined relative to the hub; the direction of the inclination of each blade is consistent.

Further preferably, the inlet installation angle of the blade is 20°˜40°.

Further preferably, the ratio of the arc length of the arcuate segment to the length of the straight segment is 1:2.5.

Further preferably, each group of the blade assemblies includes a reinforcement plate for strengthening the strength of the blade; the reinforcement plate is located between two adjacent blades and is vertically connected to the two blades; the reinforcement plate is along the The blade extends from the blade head to the blade tail; one end of the reinforcing plate near the blade head is in a circular arc shape.

Further preferably, the reinforcing plate is 0.618 times the length of the blade width from the side of the blade facing away from the inlet end of the impeller.

Further preferably, two groups of the blade assemblies are arranged, and the two groups of the blade assemblies are coaxially arranged opposite to each other; a disc is shared between two adjacent blade assemblies; both ends of the impeller are intake ends, and the two A wheel cover is provided on the side of the blade assembly located at the inlet end of the impeller.

A high specific rotational speed energy-saving centrifugal dust-removing fan adopts any one of the centrifugal impellers described in claims 1-6.

Further preferably, it includes: adopting the centrifugal impeller described in claim 6; a casing body, two sides of which are respectively provided with air intake boxes, and the two sides of the casing main body are connected to the inlet and outlet through the first air inlet. The air box is communicated with the air box; the centrifugal impeller is arranged in the main body of the casing, and the air inlet ends thereof are respectively communicated with the first air inlet through the collector; the rotating shaft passes through the main body of the casing, the air flow device, the centrifugal impeller, and connected with the driving device; the air flow passes through the air inlet box, the first air inlet, the collector, and the air inlet end of the centrifugal impeller in sequence, and then flows from The radial outlet end of the centrifugal impeller and the radial outlet of the casing body are output.

Further preferably, the inlet of the air intake box is rectangular, and the aspect ratio of the rectangle is 1:4.

Further preferably, an adjusting door for adjusting the gas flow is provided at the inlet of the air intake box, and the adjusting door includes a plurality of adjusting door blades.

Further preferably, the adjusting door blade is a shuttle-shaped hollow blade.

Further preferably, the number of blades of the regulating door and the number of blades of the centrifugal impeller are mutually prime numbers.

Further preferably, the number of blades of each group of the blade assemblies is 12 or 16, and the number of the adjustment door blades provided in each of the multi-leaf adjustment doors is 5 or 7.

The present invention provides a centrifugal impeller and a high-specific rotational speed energy-saving centrifugal dust-removing fan, which has the following advantages and positive effects compared with the prior art:

The factors of fan performance characteristics depend on the gas flow inside the fan impeller, and the internal gas flow affecting the impeller mainly depends on the form of the blade, including the blade profile, the blade inlet and outlet installation angle, the number of blades and other parameters; Operating under the design conditions, when the gas enters the blade flow channel formed between two adjacent blades, it forms a certain angle with the blade and enters the blade flow channel. The angle is smaller than or larger than the blade inlet installation angle A1. The larger the offset, the more severe the separation of the boundary layer. Due to the existence of this angle, the airflow generates a vortex on the suction surface 305 of the blade, the absolute velocity of the airflow and the relative velocity of the airflow on the back side 306 of the blade are low, and the vortex air mass is easily adhered to the back side 306 of the blade, which not only affects the performance of the fan, It can cause airflow disturbance loss, and also generate noise; it can be seen from the simulation diagrams (see Figure 8 and Figure 9) that the vortex air mass is generally formed in the area of the trailing edge 307 of the suction surface of the blade, and the vortex in these places is higher than that in other places. more serious.

1. In the centrifugal impeller of the present invention, along the direction from the blade head to the blade tail of the blade, the blade is a blade type including a combination of arc segments and straight segments, which is beneficial to ensure that the inflow direction of the airflow and the blade inlet angle A1 are maintained as much as possible. Therefore, the trend of boundary layer separation can be effectively controlled. It can be seen from the simulation diagram (see Figure 10) that the average flow velocity in this boundary layer is faster than that in the thicker boundary layer with the arc-shaped airfoil. The airflow deposition phenomenon of the blade is also much lag than that of the arc blade, and the separation of the boundary layer is effectively controlled to avoid the formation of a vortex on the trailing edge 307 of the suction surface 305 of the blade. When the impeller rotates, due to the weakening of the airflow vortex on the suction surface 305, the adhesion phenomenon of the vortex air mass at the outlet of the suction surface 305 of the blade is greatly improved, which can ensure the long-term stable operation of the impeller and avoid airflow loss, thereby obtaining a larger airflow and meet the requirements of low noise.

2. According to the computer simulation test, referring to FIG. 11 , when the arc length of the front arc segment 301 and the length of the straight segment 302 are 1:2.5, the air scouring effect is better and the fan performance is improved. The impeller made of this type of composite blade can achieve a maximum efficiency of 88.5%.

3. In the prior art, under the premise of not increasing the structural volume of the fan, if the working efficiency of the centrifugal dust removal fan is to be improved, the rotational speed of the impeller has to be increased, but this makes the fan vibration and noise increase; The centrifugal dust removal fan adopts centrifugal impeller, which can greatly reduce the volume of the whole machine while increasing the specific speed, reduce the structural cost, effectively improve the airflow delivered by the fan, and fill the large flow and medium pressure type of the national standard centrifugal fan. The blank in the spectrum meets the higher requirements of ultra-clean emission on the performance of the dust removal fan, and at the same time realizes the requirements of high efficiency, energy saving and low noise of the dust removal fan.

Description of drawings

The above and other features and advantages of the present invention will be more clearly understood from the following detailed description in conjunction with the accompanying drawings, wherein:

1 is a schematic diagram of a centrifugal impeller in Embodiment 1 of the present invention;

Fig. 2 is the schematic diagram of the centrifugal impeller with the wheel cover removed in Fig. 1;

Fig. 3 is the top view of Fig. 2;

4 is a schematic structural diagram of a centrifugal dust removal fan in Embodiment 2 of the present invention;

5 is a cross-sectional view of a centrifugal dust-removing fan in Embodiment 2 of the present invention;

6 is a schematic structural diagram of the adjusting door blade in Embodiment 2 of the present invention;

Fig. 7 is the left side view of Fig. 6;

8 is a schematic diagram of a vortex flow of a circular arc backward inclined blade in the prior art;

FIG. 9 is a schematic diagram of a vortex flow of a straight plate backward inclined blade in the prior art;

Fig. 10 is the vortex flow schematic diagram of the blade of the centrifugal impeller in the present invention;

FIG. 11 is a simulated cloud diagram of the pressure gradient of the centrifugal impeller in the present invention.

Symbol Description:

1-Impeller; 2-Hub; 3-Blade; 301-Arc segment; 302-Straight segment; 303-Blade head; 304-Blade tail; 305-Blade suction surface; 306-Blade back surface; 307-Blade trailing edge; 4- Intake end; 5- Reinforcing plate; 6- Wheel; 7- Wheel cover; 8- Chassis body; 9- First air inlet; 10- Inlet box; 11- Inlet of air box; 12 - Adjusting door; 13 - Adjusting door blade; 14 - Collector; 15 - Main shaft; 16 - Chassis air outlet.

Detailed ways

In order to more clearly describe the embodiments of the present invention or the technical solutions in the prior art, the specific embodiments of the present invention will be described below with reference to the accompanying drawings. Obviously, the accompanying drawings in the following description are only some embodiments of the present invention. For those of ordinary skill in the art, other drawings can also be obtained from these drawings without creative efforts, and obtain other implementations.

In order to keep the drawings concise, the drawings only schematically show the parts related to the present invention, and they do not represent its actual structure as a product. In addition, in order to make the drawings concise and easy to understand, in some drawings, only one of the components having the same structure or function is schematically shown, or only one of them is marked. As used herein, "one" not only means "only one", but also "more than one".

1-3, the present embodiment provides a centrifugal impeller 1, including: a hub 2 for installing a rotating shaft; at least one group of blade assemblies is provided on the hub 2, and each group of blade assemblies includes a number of blades along the circumferential direction of the hub 2 The surrounding blade 3; along the direction from the blade head 303 to the blade tail 304 of the blade 3, the blade 3 includes an arcuate segment 301 and a straight segment 302, and the straight segment 302 is radially inclined relative to the hub 2; each blade 3 is inclined the same direction.

In the centrifugal impeller 1 of the present invention, along the direction from the blade head 303 to the blade tail 304 of the blade 3, the blade 3 is a blade type including a combination of arc segments 301 and straight segments 302, which is conducive to ensuring the inflow direction of the airflow and the The blade inlet angle A1 remains the same, so that the trend of boundary layer separation is effectively controlled. It can be seen from the simulation diagram (refer to Figure 10) that the average flow velocity in this boundary layer is higher than that in the thicker boundary layer in the case of the arc-shaped airfoil. This kind of uneven airflow deposition phenomenon is also much lag than that of the arc-shaped blade, and the separation of the boundary layer is effectively controlled to avoid the formation of vortices on the trailing edge 307 of the suction surface 305 of the blade. When the impeller rotates, due to the weakening of the airflow vortex on the suction surface 305, the adhesion phenomenon of the vortex air mass at the outlet of the suction surface of the blade is greatly improved, which can ensure the long-term stable operation of the impeller and avoid airflow loss, so as to obtain a larger airflow and achieve low noise requirements.

Further, in this embodiment, referring to FIGS. 1-3 , from the tip 303 of the blade 3 to the tail 304 of the blade, the width of the arcuate segment 301 of the blade 3 gradually extends toward the inlet end of the impeller and increases to be the same as the straight segment. 302 is equal in width, so that the blade head 303 of the blade is parabolic, so that the gas is obliquely inserted into the blade flow channel between the two blades 3 when the blade rotates, and the suction capacity of the impeller is increased. Of course, in other embodiments, the shape of the blade tip is not limited to the above, and the shape of the blade tip can be changed according to specific needs.

In this embodiment, referring to FIG. 3 , the inlet installation angle A1 of the blade is 20°˜40°. The inlet installation angle A1 of the blade is the angle between the tangent at the blade inlet and the circumferential direction. Select a reasonable inlet installation angle to ensure that the inflow direction of the airflow is consistent with the inlet angle of the blade, or slightly larger than the inlet of the blade. angle. The preferred inlet installation angle of the blade in this embodiment is 22°, so that there is no offset between the airflow and the blade when the airflow flows in, the impact loss at the airflow inlet is reduced, and the tendency of boundary layer separation is effectively controlled. Of course, in other embodiments, the specific angle of the inlet installation angle is not limited, for example, the inlet installation angle may also be 30°.

In this implementation, the blades of the blade assembly are backward-facing blades, that is, the outlet installation angle A2 of the blade is less than 90°, specifically 48°. The outlet installation angle A2 of the blade is the difference between the tangential direction of the outlet end of the blade and the tangential direction of the circumference of the outlet end of the blade The bending angle of the backward blade is small, and it conforms to the movement direction of the gas under the action of centrifugal force. The impact between the air and the blade is small, so the energy loss and noise are small, and the efficiency is high. Of course, in other embodiments, the size of the outlet installation angle of the blade is not limited to the above, for example, it can also be greater than 90°, so that the blade of the blade assembly is a forward-facing blade.

In this embodiment, referring to FIG. 3 , the preferred ratio of the arc length of the arc segment 301 to the length of the straight segment 302 is 1:2.5. When the ratio is 1:2.5, the air scouring effect is the best, which is beneficial to improve the performance of the fan, and the highest efficiency can reach 88.5%. Of course, in other embodiments, the ratio of the arc length of the arc segment to the length of the straight segment is not limited to the above, and the ratio can be adjusted reasonably according to the actual situation.

In this embodiment, referring to FIGS. 1 and 2 , each group of blade assemblies includes a reinforcing plate 5 for strengthening the strength of the blade; the reinforcing plate 5 is located between two adjacent blades 3 and is vertically connected to the two blades 3 . It is beneficial to improve the rigidity of the blade and avoid the impeller imbalance caused by the "V"-shaped bending of the blade due to insufficient rigidity. When entering the flow channel between the two blades, the extending direction of the reinforcing plate is consistent with the airflow direction, so as to prevent the reinforcing plate 5 from affecting the airflow direction; the end of the further reinforcing plate 5 located near the blade head 303 is arc-shaped. The arc has little influence on the airflow. Of course, in other embodiments, the specific structural shape of the reinforcing plate is not limited to the above or shown in the drawings, and the structural shape of the reinforcing plate can be adjusted according to the actual situation.

Further, in this embodiment, referring to FIGS. 1 and 2 , in the direction of the blade width, the reinforcing plate 5 is separated from the side edge of the blade facing away from the inlet end 4 of the impeller by a length of 0.618 times the blade width, that is, the reinforcing plate 5 It is arranged on the side close to the inlet end 4 of the impeller, and the position of 0.618 times the blade width is the golden separation position of the blade 3, and the reinforcement plate is welded at the golden separation position, which effectively improves the rigidity of the blade 3 and makes the blade less stressed ; And when the air flow is sucked into the impeller 1 from the inlet end 4 of the impeller, the air flow produces a stronger impact force on the side of the blade 3 close to the inlet end, so that the reinforcing plate 5 is set here, which can effectively prevent the blade from being overstressed. deformation or vibration occurs. Of course, in other embodiments, the location where the reinforcing plate is arranged is not limited to what is described above or shown in the drawings, for example, it can also be arranged in the middle of the blade along the blade width direction.

According to the suction mode of the impeller, it is divided into a single suction impeller and a double suction impeller. When only one end of the impeller is the intake end, it is a single suction impeller; when both ends of the impeller are the intake end, it is a double suction impeller;

According to whether the impeller has a wheel cover 7 and a wheel disc 6, it is divided into three types of impellers: fully open, semi-open and fully closed.

For example, in this embodiment, referring to Figures 1-3, two sets of blade assemblies are provided, and the two sets of blade assemblies are coaxially arranged opposite to each other; a disc 6 is shared between two adjacent blade assemblies; both ends of the impeller are intake ends 4. A wheel cover 7 is provided on one side of the two blade assemblies located at the inlet end 4 of the impeller, forming a fully closed double suction impeller.

Of course, in other embodiments, the structure of the centrifugal impeller is not limited to the one described in this embodiment, and there are various classification and deformations. For example, on the basis of the embodiment, the wheel cover 7 on the blade assembly is removed to form a half Open double suction impeller; on the basis of the embodiment, the wheel cover 7 and the wheel disc 6 on the blade assembly are removed to form a fully open double suction impeller;

Of course, in other embodiments, the number of blade assemblies is not limited to the above. For example, on the basis of this embodiment, one group of blade assemblies is removed, that is, only one group of blade assemblies is provided, and one end of the blade assembly is the part of the impeller. The intake end 4, thus the hub 2 and a set of the set of blade assemblies together form a fully closed single suction impeller. The wheel cover 7 is further removed to form a semi-open single suction impeller.

Example 2

This embodiment provides a high-specific-speed energy-saving centrifugal dust-removing fan, which adopts any one of the centrifugal impellers described above.

In this embodiment, the double suction impeller in Embodiment 1 is used as an example, and the specific structure of a high specific speed energy-saving centrifugal dust removal fan and the excellent effects produced are described in detail. Of course, in other embodiments, other types of centrifugal impellers described above can also be used.

Referring to Figure 4-7, the high specific speed energy-saving centrifugal dust removal fan further includes:

The casing body 8 is provided with air intake boxes 10 on both sides respectively, and the two sides of the casing body 8 are communicated with the air intake box 10 through the first air inlet 9;

The double suction impeller 1 is arranged in the casing main body 8, and the air inlet ends 4 thereof are respectively communicated with the first air inlet 9 through the collectors 14;

The rotating shaft 15 runs through the casing body 8, the current collector 14, and the double suction impeller 1 in sequence, and is connected with the driving device;

The airflow passes through the air inlet box 10, the first air inlet 9, the collector 14, and the air inlet end 4 of the double suction impeller 1 in sequence, and then flows from the radial outlet end of the double suction impeller 1 to the radial outlet of the casing body. 16 outputs.

The centrifugal dedusting fan provided in this embodiment adopts a centrifugal impeller, which can greatly reduce the volume of the whole equipment while increasing the specific speed, effectively improve the airflow delivered by the fan, and fill the large flow and medium pressure in the national standard centrifugal fan. The blank in the type spectrum meets the higher requirements of ultra-clean emission on the performance of the dust removal fan, and at the same time realizes the high efficiency, energy saving and low noise requirements of the dust removal fan.

Specifically, the casing body 8 is in the shape of a volute, and shares side plates with the air intake boxes 10 on both sides, which is beneficial to reduce the structural cost and reduce the axial size of the fan; Reinforcing rib plates with suitable spacing and height can greatly improve the rigidity of the casing and effectively resist the aerodynamic disturbance of the casing when the impeller rotates.

Further, in this embodiment, the current collector 14 is an arc-shaped current collector, and the current collector gradually converges along the axial direction to approximate the shape of an arc. The arc-shaped current collector is conducive to reducing airflow loss and guiding airflow into The flow condition of the impeller is better. Of course, in other embodiments, a cylindrical collector or a conical collector can also be used.

Further, in this embodiment, the inlet of the air intake box 10 is preferably rectangular, and the aspect ratio of the rectangle is 1:4, wherein the length of the rectangle is the side extending along the axial direction of the main shaft, so as to ensure the centrifugal dust removal fan. With the best gas flow efficiency, the axial size of the centrifugal dust collector should be reduced as much as possible, thereby reducing the overall size of the fan. After many experiments and calculations, it is concluded that when the inlet aspect ratio of the intake box is 1:4, the flow efficiency of the airflow is the highest; when the aspect ratio is less than 1:4, such as 1:5, when the airflow passes through the intake air After the box, the airflow changes from radial flow to axial flow and turns into the impeller, resulting in rapid airflow loss and affecting airflow performance; when the aspect ratio is greater than 1:4, such as 1:2, the shaft of the fan As the size increases, the overall size of the fan is increased, and the floor space cannot be saved. Of course, in other embodiments, the aspect ratio of the inlet of the intake box is not limited to the above.

In this embodiment, an adjusting door 12 for adjusting the gas flow is provided at the inlet of the air intake box 10 , and the adjusting door 12 includes a plurality of adjusting door blades 13 . Leaf flap type differential adjustment door, the adjustment door blade 13 is generally driven by a rolling bearing with a diamond seat, and the multiple adjustment door blades 13 are turned to adjust the gas flow into the intake box, and the adjustment process is flexible and labor-saving. Of course, in other embodiments, the type of the adjusting door is not limited to the above, for example, a circular petal adjusting door may also be used.

Further, in this embodiment, referring to FIGS. 6 and 7 , the preferred regulating door blade 13 is a shuttle-shaped hollow blade, which has less resistance to airflow and better airflow performance. Of course, in other embodiments, the specific structural form of the adjusting door blade is not limited to the above.

In this embodiment, the number of adjusting door blades 13 and the number of blades 3 of the double suction impeller are mutually prime numbers. If there is a common divisor between the two, when the airflow flows from the intake box into the impeller, the airflow coupling vibration will occur, which will consume airflow energy, reduce the wind pressure, and cause the airflow to pulsate, causing the fan to generate mechanical vibration and noise, affecting its service life.

Further, the number of blades of the impeller is an important parameter directly related to the aerodynamic performance of the fan. Too few blades will cause secondary eddy currents in the impeller flow channel, resulting in pressure loss; while too many blades will reduce the effective flow area of the gas. The impact loss at the inlet of the impeller and the friction loss along the way are increased, and the load of the impeller main shaft will be increased, and the total pressure and efficiency of the fan will be reduced. When there are 14 or 16 blades, the fan efficiency is higher. In this embodiment, through experimental calculation, it is concluded that when the number of blades in each group of blade assemblies is 12 or 16 blades, the airflow performance of the centrifugal dust removal fan is optimal at this time. ; The number of regulating door blades 13 and the number of blades 3 of the impeller are mutually prime numbers, so that the number of regulating door blades 13 provided by each multi-leaf regulating door is 5 or 7. Of course, in other embodiments, the number of impeller blades is set The number of setting and adjusting door blades is not limited to the above, and can be adjusted reasonably according to the actual application.

In order to fully demonstrate the advantages of a centrifugal dust removal fan provided by the present invention, under the premise of the same full pressure, the same output dust removal air volume, and the same specific rotational speed, the following adopts the 4-73 series fans in the prior art ( For example, the centrifugal dust removal fan of model 4-73 No. 24.5F, in which 4 means the pressure coefficient is grade 4, and 73 is the specific speed of the fan) and the performance of the same type of centrifugal dust removal fan in the present invention is compared and analyzed (where the same type means the same pressure coefficient, the specific speed can reach more than 73 large air volume fans):

For example: the design parameters of a steel-making desulfurization and dust removal fan after ultra-clean discharge are: atmospheric pressure 101325Pa, dust removal air volume Q=900,000 m3/h, total pressure Pt=5000Pa, fan inlet pressure Pin=-4500Pa, medium temperature t=120℃ , medium density ρ=1.293kg/Nm3, working condition density ρv=0.853kg/m3.

The following table shows the dimensioned performance comparison of the two fans: (fan speed n=960rpm)

It can be seen from the above table that, under the premise of satisfying the same flow rate, full pressure and specific speed, the centrifugal dust removal fan in the present invention is 3.68% more efficient than the 4-73 No. 24.5F fan in the prior art, and the effective power of the fan is improved by 3.68%. Reduced by 2.41%, and the diameter of the fan impeller of the present invention is reduced by 100mm, and the volume of the fan is reduced, which not only reduces materials and saves manufacturing costs, but also reduces the flywheel torque of the impeller rotor, shortens the fan start-up time, and increases the first-order critical speed of the rotor. Enhance the reliability of the fan rotor.

Then compare the inlet and outlet area ratios of the two fans:

It can be seen from the above table that the fan provided by the present invention can provide higher static pressure than the fan of type 4-73No. 24.5F in the prior art, satisfying the same flow rate and full pressure. In other words, to meet the same static pressure value, the fan using this patent can choose a smaller volume and better performance. The static pressure is a sign of the ability of the fan to overcome the resistance along the pipe network and the local resistance of the system.

Based on the above comparison results, in other words, on the premise that the fan design rotational speed is equal, among the same type of fans, the centrifugal dust removal fan of the present invention provides a larger dust removal air volume, a higher specific speed that can be achieved, and a smaller external dimension. Reduce structural costs.

The embodiments of the present invention have been described in detail above with reference to the accompanying drawings, but the present invention is not limited to the above-mentioned embodiments. Even if various changes are made to the present invention, if these changes fall within the scope of the claims of the present invention and the technical equivalents thereof, they still fall within the protection scope of the present invention.

Claims (13)

1. A centrifugal impeller, characterized in that it comprises: a hub for installing a rotating shaft; at least one group of blade assemblies is provided on the hub, and each group of the blade assemblies comprises a plurality of blade; Along the direction from the blade head to the blade tail of the blade, the blade includes an arcuate segment and a straight segment, and the straight segment is radially inclined relative to the hub; the direction of inclination of each blade is consistent. 2 . The centrifugal impeller according to claim 1 , wherein the inlet installation angle of the blade is 20°˜40°. 3 . 3. The centrifugal impeller according to claim 1, wherein the ratio of the arc length of the arcuate segment to the length of the straight segment is 1:2.5. 4 . The centrifugal impeller according to claim 1 , wherein each group of the blade assemblies includes a reinforcing plate for strengthening the strength of the blades; the reinforcing plate is located between two adjacent blades and is connected with the blades. 5 . The two blades are connected vertically; the reinforcing plate extends along the direction from the blade head to the blade tail of the blade; one end of the reinforcing plate near the blade head is in a circular arc shape. 5 . The centrifugal impeller according to claim 4 , wherein in the direction of the blade width, the reinforcing plate is separated from the side of the blade facing away from the inlet end of the impeller by a length of 0.618 times the blade width. 6 . 6 . The centrifugal impeller according to claim 1 , wherein two groups of the blade assemblies are arranged, and the two groups of the blade assemblies are coaxially arranged opposite to each other; a disc is shared between the two adjacent blade assemblies. 7 . Both ends of the impeller are intake ends, and a wheel cover is provided on one side of the two blade assemblies located at the intake end of the impeller. 7. A high specific rotational speed energy-saving centrifugal dust-removing fan, characterized in that any one of the centrifugal impellers described in claims 1-6 is adopted. 8. The high specific rotational speed energy-saving centrifugal dust-removing fan according to claim 7, characterized in that, comprising: Adopt the centrifugal impeller described in claim 6; The casing body, two sides of which are respectively provided with air intake boxes, and the two sides of the casing body are communicated with the air intake boxes through the first air inlet; The centrifugal impeller is arranged in the main body of the casing, and the air inlet ends thereof are respectively communicated with the first air inlet through the collectors; a rotating shaft, which runs through the casing body, the current collector, and the centrifugal impeller in sequence, and is connected with the driving device; The airflow passes through the air inlet box, the first air inlet, the collector, and the air inlet end of the centrifugal impeller in sequence, and then flows from the air outlet end in the radial direction of the centrifugal impeller to the casing. The air outlet in the radial direction of the body is output. 9 . The high specific rotational speed energy-saving centrifugal dust removal fan according to claim 8 , wherein the inlet of the air intake box is rectangular, and the length-width ratio of the rectangle is 1:4. 10 . 10 . The high specific speed energy-saving centrifugal dedusting fan according to claim 8 , wherein an adjusting door for adjusting the gas flow is provided at the entrance of the air intake box, and the adjusting door comprises a plurality of adjusting door blades. 11 . . 11 . The high specific rotational speed energy-saving centrifugal dust removal fan according to claim 10 , wherein the regulating door blade is a shuttle-shaped hollow blade. 12 . 12 . The high specific rotational speed energy-saving centrifugal dust removal fan according to claim 10 , wherein the number of blades of the regulating door and the number of blades of the centrifugal impeller are mutually prime numbers. 13 . 13 . The high specific speed energy-saving centrifugal dust removal fan according to claim 12 , wherein the number of blades in each group of the blade assemblies is 12 or 16, and the The number of adjustable door blades is 5 or 7.

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