An impeller and a voluteless fan having the same

Abstract

The application relates to the technical field of fans, in particular to an impeller and a volute-free fan with the same, the volute-free fan comprising, in sequence along the Z-axis direction, an air inlet mounting panel, the impeller, a motor and a fan mounting panel, the air inlet mounting panel being provided with an air inlet, the air inlet being connected with one end of the impeller in a matched mode to form a gradually expanding airflow channel, and each parameter of the impeller being optimized in design. The application is verified through a sand dust test, and under the same conditions, the dust accumulation amount is reduced by 86%, the influence of dust accumulation on the rotor unsteadiness of the fan is greatly reduced, and the equipment maintenance cycle and service life are significantly prolonged.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of fans, in particular to a three-dimensional flow anti-dust accumulation impeller and a three-dimensional flow anti-dust accumulation voluteless fan with the same. BACKGROUND

[0002] As a core key equipment of the ventilation and cooling system of a rail transit vehicle, the long-term stable operation of a centrifugal fan directly determines the environmental comfort in the vehicle cabin and has an important influence on the operation safety of various core equipments of the vehicle, and is one of the basic components for ensuring the reliable operation of the rail transit vehicle.

[0003] In the prior art, the impeller blades of the centrifugal fan are mostly of a single plate type or a simple circular arc type structure, and the flow channel design does not fully consider the three-dimensional flow field characteristics in the actual operation process of the rail transit fan, resulting in that the airflow is easy to form a stable negative pressure vortex area in the non-working surface of the blade (especially in the area of the front disc of the impeller). The negative pressure vortex area will form a strong dust particle capture effect and become the main area of dust adhesion; when the dust accumulation reaches a certain thickness, uneven shedding phenomenon is easy to occur, thereby destroying the dynamic balance of the impeller and causing severe vibration of the fan, which not only leads to a significant increase in wind resistance and an abnormal rise in motor load, but also causes the fan to stop running in severe cases, directly affecting the normal operation of the rail transit vehicle. In view of the above dust accumulation problem, the prior art solutions mostly adopt a passive protection mode of installing block-shaped protrusions or anti-dust accumulation plates on the surface of the blade. Although this kind of solution can reduce dust adhesion in local areas, it will greatly destroy the continuity of the flow field inside the fan, resulting in a significant decrease in the operating efficiency of the fan, and its design does not fully adapt to the unique voluteless structure characteristics of the rail transit fan, which has poor installation compatibility, unstable anti-dust accumulation effect and other defects, and is difficult to meet the actual application requirements. At the same time, although the three-dimensional flow impeller technology has been applied in the field of industrial fans and has been proved to be able to improve the operating efficiency of the fan by precisely optimizing the flow field distribution, up to now, there is still no technical solution that combines the three-dimensional flow impeller technology with the structure of the rail transit voluteless fan to control dust accumulation from the root of the flow field, which cannot meet the dual requirements of high-efficiency operation and dust accumulation improvement.

[0004] Therefore, there is an urgent need for a fan structure that takes into account both high-efficiency operation and dust accumulation improvement, controls dust accumulation from the root of the flow field by optimizing the design of the impeller, and meets the stringent requirements of the rail transit field for high reliability and low operation and maintenance cost of equipment. SUMMARY

[0005] The purpose of the present application is to provide an impeller and a voluteless fan with the same, to solve the problems of serious dust accumulation of the impeller in the field of rail transit, and serious dust accumulation and low operating efficiency of the voluteless fan due to poor structure adaptability and unreasonable flow field design of the impeller in the prior art.

[0006] The embodiments of the present application can be implemented by the following technical solutions:

[0007] A kind of impeller, including impeller front disc, impeller rear disc and several ternary flow blades connected between the impeller front disc and the impeller rear disc, along the direction of Z axis, the space between the two profile lines of the impeller front disc and the impeller rear disc is equally divided into 4 space volumes equal small flow channels, form 5 different small flow channel lines a, b, c, d, e, wherein a is front disc profile line, e is rear disc profile line, the intersection of the 5 lines with the same ternary flow blade is 、 、 、 、 , 、 、 、 、 The projection line i on the cross section perpendicular to Z axis is respectively recorded as 、 、 、 、 ;

[0008] Specific design parameter range is as follows,

[0009]

[0010] Wherein, the curved surface of the ternary flow blade and the impeller front disc is connected and the front blade root, the outlet edge diameter of the front blade root is blade outlet edge diameter The straight line distance of i number projection line at the end point of outlet edge to the center of fan rotating shaft is outlet projection diameter The distance of the inlet edge end point of i number projection line to the projection axis center is inlet projection diameter The angle between the tangent of the inlet edge end point of i number projection line and the tangent of the circular arc of the end point of projection axis center is projection inlet angle The angle between the tangent of the outlet edge end point of i number projection line and the tangent of the circular arc of the end point of projection axis center is projection outlet angle .

[0011] Further, along the flow direction of air flow from air inlet to air outlet, the angle between i number projection line and the circumferential angle difference of the corresponding two radii of outlet edge formed by its adjacent projection line is stagger angle , 、 、 、 The design parameter range of the stagger angle of 0-6, 0-5, 0-4, 0-3.

[0012] Furthermore, the impeller front disc is composed of a tangent front disc arc segment and a front disc straight segment, wherein the forming angle of the front disc straight segment is... The range is 0°-25°, the ratio of the inlet projection diameter D04 of the impeller front plate to the outlet outer diameter D05 of the impeller front plate is 0.65-0.8, and along the Z-axis direction, the ratio of the height H05 of the impeller front plate to the height H07 of the impeller is 0.3-0.6.

[0013] Furthermore, the impeller rear disk is composed of a first straight segment, a first arc segment, a second straight segment, and a second arc segment connected in sequence, wherein the forming angle of the second straight segment is... The range is 15°-35°; the ratio of the center diameter D06 of the rear disc center hole to the outlet outer diameter D05 of the front disc of the impeller is 0.3-0.5; the ratio of the outer edge diameter D07 of the rear disc to the outlet outer diameter D05 of the front disc of the impeller is 0.8-1; the ratio of the height H06 of the rear disc to the height H07 of the impeller is 0.4-0.75; the ratio of the height H07 of the impeller to the outlet outer diameter D05 of the front disc of the impeller is 0.21-0.35.

[0014] Furthermore, the curved surface connecting the three-dimensional flow blade to the impeller front disk is the front blade root, and the outlet edge diameter of the front blade root is... The ratio of the outer diameter D05 of the impeller front disc to the outlet diameter D05 ranges from 0.48 to 0.493.

[0015] Furthermore, the number of the three-dimensional flow blades is 7-15.

[0016] Furthermore, the outlet edge of the three-dimensional flow blade is provided with several serrations to... This indicates the length of the exit edge of the three-dimensional flow blade. This indicates the spacing between two adjacent saw teeth. Specifically, there are no saw teeth in the one-third area closest to the outlet edge of the impeller front disc, and the saw teeth are only arranged in the remaining two-thirds area. The spacing between two adjacent saw teeth... The length of the outlet edge of the three-dimensional flow blade The ratio ranges from 0.11 to 0.15.

[0017] A volute-less fan includes an impeller as described above, and also includes an air inlet mounting panel, a motor, and a fan mounting panel connected along the vertical rotation axis Z-axis.

[0018] The air inlet mounting panel is provided with an air inlet, which is connected to one end of the impeller to form a gradually expanding airflow channel;

[0019] The air inlet comprises an air inlet neck section, the air inlet neck section is composed of a circular arc section and a straight line section, the straight line section is tangent to the circular arc section; wherein the ratio of the air inlet diameter D01 to the air outlet diameter D02 of the air inlet is in the range of 1.02-1.6.

[0020] Further, the minimum diameter of the air inlet is the throat diameter D03, the ratio of the throat diameter D03 of the air inlet to the air outlet diameter D02 of the air inlet is in the range of 0.92-0.95, and the ratio of the throat diameter height H02 to the air inlet height H01 is in the range of 0.35-0.5.

[0021] Further, the overlap depth of the impeller front disc and the air inlet is 5-10mm, and the overlap gap is 1-4mm.

[0022] The embodiment of the application provides a kind of impeller and voluteless fan at least has the following beneficial effects:

[0023] The application constructs collaborative dust prevention system through multi-dimensional structure optimization, significantly improves the dust accumulation capacity of impeller: by accurately designing / 、 / 、 、 And other parameters, make the flow passage form smooth diffuser flow field, flow velocity changes gently without mutation, reduce the formation of negative pressure vortex area from the root; The sawtooth structure of specific size ratio is used at the blade outlet edge, which cuts the stable vortex at the tail into easy-to-dissipate micro-vortex, destroys the flow field conditions for continuous dust adhesion, and at the same time, the impact force of airflow adhesion flow continuously scours the surface of blade; The overlap depth and gap of the impeller and the air inlet are optimized, and the reasonable blade spacing design is used to avoid the occurrence of low flow area or dead zone in the flow passage, enhance the airflow dust carrying capacity, and ensure that dust is quickly discharged with the main flow; Superimposed multiple insulation structures block the electrochemical corrosion caused by stray current, reduce the adsorption of dust on the corrosion surface, and finally verified by sand and dust test, under the same conditions, the dust accumulation amount is reduced by 86%, which greatly reduces the influence of dust accumulation on the rotor unsteadiness of fan, significantly prolongs the equipment maintenance cycle and service life. BRIEF DESCRIPTION OF DRAWINGS

[0024] Figure 1 It is a structural schematic diagram of a voluteless fan of the application;

[0025] Figure 2 It is a side sectional structural schematic diagram of a voluteless fan of the application;

[0026] Figure 3 It is an air inlet structural schematic diagram of a voluteless fan of the application;

[0027] Figure 4 Structure diagram of the impeller in the present application;

[0028] Figure 5a Structure diagram of the impeller in the present application;

[0029] Figure 5b Structure diagram of the impeller in the present application;

[0030] Figure 6a Structure diagram of the impeller in the present application;

[0031] Figure 6b Structure diagram of the impeller in the present application;

[0032] Figure 7 Structure diagram of the impeller in the present application;

[0033] Figure 8 Structure diagram of the impeller in the present application;

[0034] Figure 9 Structure diagram of the impeller in the present application;

[0035] Figure 10 Structure diagram of the impeller in the present application;

[0036] Figure 11a Structure diagram of the impeller in the present application;

[0037] Figure 11b Structure diagram of the impeller in the present application;

[0038] Figure 12 Structure diagram of the impeller in the present application;

[0039] Figure 13a Structure diagram of the impeller in the present application;

[0040] Figure 13b Structure diagram of the impeller in the present application;

[0041] Figure 14a Structure diagram of the impeller in the present application;

[0042] Figure 14b Structure diagram of the impeller in the present application;

[0043] Figure 15aFigure 6 is a vector diagram of fan speed in the impeller region for the front disc of the prior art comparative example;

[0044] Figure 15b Figure 7 is a vector diagram of fan speed in the vicinity of the rear disc for the prior art comparative example.

[0045] Figure 6 is a vector diagram of fan speed in the impeller region for the front disc of the prior art comparative example;

[0046] 1 - inlet mounting panel; 2 - front disc of impeller; 3 - rear disc of impeller; 4 - three-dimensional flow blade; 5 - shaft sleeve; 6 - motor; 7 - motor connecting support; 8 - fan mounting panel; 9 - panel reinforcing frame; 10 - inlet; 11 - inlet connecting support; 12 - inlet gasket; 13 - inlet insulation plate; 14 - panel gasket; 15 - panel insulation pad; 16 - connecting piece;

[0047] 101 - inlet flange; 102 - inlet neck section; 103 - large-diameter through hole; 104 - small-diameter through hole;

[0048] 105 - circular arc section; 106 - straight line section; 201 - arc section of front disc; 202 - straight line section of front disc; 301 - first straight line section of rear disc; 302 - second straight line section of rear disc; 303 - second arc section of rear disc; 304 - first arc section of rear disc. DETAILED DESCRIPTION

[0049] Hereinafter, the present application will be further described based on preferred embodiments and with reference to the accompanying drawings.

[0050] In addition, for the convenience of understanding, various components on the drawings are enlarged or reduced, but such a practice is not intended to limit the scope of protection of the present application.

[0051] The singular form also includes the plural meaning, and vice versa.

[0052] In the description of the embodiments of the present application, it should be noted that if the terms "upper", "lower", "inner", "outer" and the like indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the drawings, or the orientation or positional relationship of the product of the embodiments of the present application when it is usually placed, and are only for the convenience of describing the present application and simplifying the description, and therefore cannot be understood as indicating or implying that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as limiting the present application. In addition, in the description of the present application, in order to distinguish different units, the first, second and the like are used in the specification, but these are not limited by the order of manufacture, and cannot be understood as indicating or implying relative importance, and the name may be different in the detailed description and claims of the present application.

[0053] The words in the specification are used to describe the embodiments of the present application, but are not intended to limit the present application. It should be noted that, unless otherwise specified and limited, if the terms "arranged", "connected", "linked" appear, they should be understood broadly, for example, can be fixedly connected, can be detachably connected, or integrally connected; can be mechanically connected, can be directly connected, or indirectly connected through an intermediate medium, can be connected inside two elements. For those skilled in the art, the specific meaning of the above terms in the present application can be understood specifically.

[0054] For ease of description, the direction of the rotating shaft of the fan is marked as the Z-axis, wherein the airflow flows from the negative direction side of the Z-axis (the air inlet end) to the positive direction side of the Z-axis (the air outlet end, close to the impeller side) along the axial direction.

[0055] Specifically, as shown in Figure 1 , Figure 2 A volute-free fan includes an air inlet mounting panel 1, an impeller, a motor 6, and a fan mounting panel 8 connected in sequence along the Z-axis direction. The air inlet mounting panel 1 is provided with an air inlet 10, which is connected with one end of the impeller to form a gradually expanding airflow passage. The airflow first passes through a straight section to stabilize the airflow, and then passes through a circular arc section for smooth transition. The above design with the straight section in front can stabilize the airflow from the source, avoid airflow turbulence at the inlet end, and reduce airflow impact during turning. There is no obvious airflow mutation throughout the process, which reduces the formation of negative pressure vortex area from the root of the flow field and significantly reduces the risk of dust adhering to the non-working surface of the blade and the front disc of the impeller.

[0056] The gradually expanding airflow passage is achieved through the following structural design:

[0057] In some preferred embodiments, as shown in Figures 1 to 3 The air inlet 10 includes an air inlet neck section 102, which is composed of a circular arc section 105 and a straight section 106, and the straight section 106 is tangent to the circular arc section 105. The ratio of the air inlet diameter D01 of the air inlet 10 to the air outlet diameter D02 of the air inlet 10 is in the range of 1.02-1.6, the minimum diameter of the air inlet 10 is the throat diameter D03, the ratio of the throat diameter D03 of the air inlet 10 to the air outlet diameter D02 of the air inlet 10 is in the range of 0.92-0.95, and the ratio of the throat diameter height H02 to the air inlet height H01 is in the range of 0.35-0.5. If the above ratio is too small, the turning radius of the airflow is small, the flow loss is large, the guiding effect of the air inlet on the airflow is weakened, and the high efficiency area of the performance curve is narrowed. If the ratio is too large, the airflow enters the throat of the air inlet from the outside domain, the flow velocity rapidly increases in a short distance, the flow loss increases, and the airflow is prone to separation before entering the impeller.

[0058] In some preferred embodiments, the air inlet 10 of the fan has a structure that expands outward at both ends and is concave in the middle. The air inlet diameter D01 refers to the port diameter at the airflow inlet end, the air outlet diameter D02 refers to the port diameter at the airflow outlet end, and the throat diameter D03 refers to the minimum cross-sectional diameter of the concave area in the middle.

[0059] In some preferred embodiments, such as Figure 4 As shown, the impeller includes a front impeller plate 2, a rear impeller plate 3, and several three-dimensional flow blades 4. The front impeller plate 2 is connected to the air inlet 10. The rear impeller plate 3 is coaxially connected to the drive end of the motor 6. The other end of the motor 6 is fixedly connected to the fan mounting panel 8. Several three-dimensional flow blades 4 are connected between the front impeller plate 2 and the rear impeller plate 3 along the circumferential direction of the Z-axis.

[0060] In some preferred embodiments, the impeller front disc 2 is composed of a front disc arc segment 201 and a front disc straight segment 202, wherein the front disc arc segment 201 and the front disc straight segment 202 are tangent, the radius of the front disc arc segment 201 is in the range of 40mm-80mm, and the forming angle of the front disc straight segment 202 is... The range is 0°-25°. The ratio of the inlet projection diameter D04 of the impeller front plate 2 to the outlet outer diameter D05 of the impeller front plate 2 is 0.65-0.8. Along the Z-axis direction, the ratio of the height H05 of the impeller front plate 2 to the height H07 of the impeller is 0.3-0.6.

[0061] In some preferred embodiments, along the Z-axis, the impeller rear disk 3 is composed of a first straight segment 301, a first arc segment 304, a second straight segment 302, and a second arc segment 303 connected in sequence. Both arc segments of the impeller rear disk 3 are tangent to their adjacent straight segments. The radius of the second arc segment 303 ranges from 150mm to 450mm; the radius of the first arc segment 304 ranges from 10mm to 50mm; and the forming angle of the second straight segment 302 is... The range is 15°-35°; the ratio of the center diameter D06 of the rear disc center hole end of the impeller rear disc 3 to the outlet outer diameter D05 of the outer edge of the front disc of the impeller front disc 2 ranges from 0.3 to 0.5; the ratio of the outer edge diameter D07 of the rear disc of the impeller rear disc 3 to the outlet outer diameter D05 of the outer edge of the front disc of the impeller front disc 2 ranges from 0.8 to 1; the ratio of the height H06 of the impeller rear disc 3 to the height H07 of the impeller ranges from 0.4 to 0.75; the ratio of the height H07 of the impeller to the outlet outer diameter D05 of the outer edge of the front disc of the impeller front disc 2 ranges from 0.21 to 0.35.

[0062] Through the above setting, the overcurrent area curve of the airflow is obviously improved, such as Figure 6a 、 Figure 6b The comparative schematic diagram is as follows:

[0063] Figure 5a In order to change the overcurrent area curve of the front impeller, the whole curve has a protrusion and the curvature changes disorderly, which indicates that the airflow velocity distribution in the flow passage is uneven and changes sharply; the three-dimensional flow blade 4 corresponds to the region where the four points at the end of the curve are located, the curve in this region is horizontal and has a downward trend, which not only causes the flow passage itself to have no pressure boosting capability, but also causes the pressure boosting function of the three-dimensional flow blade 4 to be unable to be exerted, and at the same time, causes the airflow velocity acceleration to abnormally increase, unnecessary kinetic energy loss is caused, and turbulence is easily caused, and energy loss and dust adhesion risk are aggravated.

[0064] Figure 5b The overcurrent area curve of the fan impeller of the application is shown in the figure, and the space form is changed due to the influence of the shaft sleeve and the change of the airflow flow direction, the first half of the curve slightly decreases, and the medium is smoothly introduced into the impeller to provide pre-flow guide; the three-dimensional flow blade 4 also corresponds to the region where the four points at the end of the curve are located, the curve in this region is a parabola opening upward, and the efficient conversion of part of the airflow kinetic energy to pressure energy can be realized; the whole curve shape is natural and smooth, and follows the change trend of the quadratic function , the curvature changes gently, and there is no mutation and singular point. At the same time, the total length of the overcurrent passage is shortened, which not only reduces the disc friction loss, but also reduces the total area of the dust that can be attached, and lays a good foundation for the effective work of the three-dimensional flow blade 4 and the smooth passing of the medium in this region.

[0065] Figure 6a The vector diagram of the velocity in the flow field on the shaft section before the structure of the impeller is changed, Figure 6b The vector diagram of the velocity in the flow field on the shaft section of the fan of the application, as shown in the figure, it can be seen that the low-speed vortex area on the back of the three-dimensional flow blade 4 has disappeared obviously after the change, the flow velocity state after the gas is discharged from the impeller is significantly improved, and the uniformity of the flow field is greatly improved.

[0066] The application optimizes the design of the impeller structure, so that the overcurrent passage formed by the front disc 2 and the rear disc 3 of the impeller has excellent pressure boosting capability, the working efficiency of the impeller is significantly improved, the airflow flow velocity changes gently without mutation, the formation of vortex area is reduced from the root, the airflow velocity acceleration at the outlet of the impeller is greatly reduced, the running noise is effectively reduced, the ability of the airflow in the blade area to carry particles is significantly enhanced, and the flow field characteristics are optimized from multiple dimensions.

[0067] Specifically, the application re-designs the three-dimensional flow blade to precisely match the front and rear disc structure and the equipment operating condition, and highly adapts to the flow space characteristics; at the same time, the blade profile is optimized to promote the formation of stable wall flow of air flow on the blade surface, reduce dust adhesion by means of air flow impact force; in addition, by reasonably designing the impeller blade spacing and the inlet and outlet angles, the air flow separation phenomenon is effectively weakened, the backflow area is reduced, the particles are quickly discharged with the main air flow, the low flow area or dead area in the flow passage is avoided, and the air flow can continuously flush the surface of the blade, thereby fundamentally inhibiting dust deposition.

[0068] Further, along the direction of the vertical rotation axis Z, the space between the two profiles of the impeller front disc 2 and the impeller rear disc 3 arranged towards each other is equally divided into four small flow channel volumes, forming five different small flow channel lines a, b, c, d, e, wherein a is the front disc profile line, e is the rear disc profile line, the outlet projection diameter is as shown in Figure 7 、 Figure 8 The intersection of the five lines with the same three-dimensional flow blade 4 is as shown in 、 、 、 、 As shown in Figure 8 , 、 、 、 、 The projection line i on the cross section perpendicular to the Z axis is respectively 、 、 、 、 As shown in Figure 9 , the straight line distance from the end point of the outlet edge to the center of the fan rotation axis is the outlet projection diameter , the distance from the end point of the inlet edge of the i-numbered projection line to the axis center is the inlet projection diameter , the projection inlet angle is the included angle between the tangent of the end point of the inlet edge of the i-numbered projection line and the tangent of the circular arc passing through the end point, the projection outlet angle is the included angle between the tangent of the end point of the outlet edge of the i-numbered projection line and the tangent of the circular arc passing through the end point, the stagger angle is the circumferential angle difference between the i-numbered projection line and the projection line adjacent to the outlet edge of the i-numbered projection line, is the angle occupied by the i-numbered projection line of a single three-dimensional flow blade in the circumferential direction of the impeller, i is the position number of the projection line, and respectively 、 、 、 , The mark, the specific design parameter range is as follows:

[0069]

[0070] Wherein, the curved surface of the three-dimensional flow blade 4 connected with the impeller back disc 3 is a rear blade root, the curved surface of the three-dimensional flow blade 4 connected with the impeller front disc 2 is a front blade root, the inlet is an edge where the airflow flows in, and the outlet edge is an edge where the airflow flows out.

[0071] , It is the core key parameter for improving the blade flow condition and inhibiting dust accumulation, mainly in the following aspects.

[0072] Avoiding "inlet vortex" from the source, reducing the initial dust accumulation inducement, mainly in that: the blade inlet is the "connection point" of the airflow from the air inlet into the flow passage, if The airflow direction at the inlet radius does not match (such as Too large, the airflow "head-on" hits the blade inlet; or Too small, the airflow "circulates" around the blade inlet), which will cause the airflow to prematurely separate from the blade surface at the front disc, forming a "vortex zone". The vortex zone is a negative pressure area that will actively attract dust particles in the airflow, forming initial dust accumulation; and reasonable (Matching with the incoming flow direction) can make the airflow smoothly enter along the blade inlet profile, avoid impact and separation, eliminate the inlet vortex zone from the source, cut off the formation path of initial dust accumulation, and at the same time, can make the airflow enter the flow passage with stable flow rate, ensuring that dust particles flow smoothly with the airflow and do not settle early.

[0073] Optimizing "outlet diffuser and flow rate", inhibiting outlet dust accumulation and backflow, mainly in that: It is the core control parameter of diffuser capacity - when Designed as a reasonable acute angle (or a specific angle range), the blade outlet profile can guide the airflow to efficiently convert the "kinetic energy" obtained by rotation into "pressure energy" when leaving the blade, avoiding the formation of a negative pressure vortex zone at the outlet due to low pressure. The negative pressure vortex zone is a "heavy disaster area" for dust adhesion, especially in a wormless fan, the outlet is wormless for flow guidance, and the negative pressure vortex zone is more likely to exist stably; optimizing Can enhance the diffuser effect, eliminate or weaken the outlet negative pressure vortex zone, and reduce dust adhesion. If Too small (acute angle), the flow rate at the outlet will decrease, and the energy conversion capacity will be insufficient; if Too large, a separation zone is formed, the flow rate of the airflow will suddenly decrease, and dust particles will directly settle in the blade outlet area due to insufficient kinetic energy. Reasonable This allows the airflow to leave the blades at a gentle speed, which avoids dust impact and deposition while ensuring the airflow's ability to carry dust, thus smoothly expelling the dust from the fan and reducing dust accumulation at the blade outlet.

[0074] In addition, in the process of achieving optimal flow conditions and preventing dust accumulation on the blades, the radial proportional parameter... / (Ratio of blade inlet radius to characteristic reference radius) / (Ratio of blade exit radius to characteristic reference radius) and angular parameters (Projection entrance angle) The (projected exit angle) is an interconnected parameter system: the radial proportional parameter provides the "spatial boundary" for the angle parameter, while the angle parameter provides "direction and path guidance" for the airflow within the radial space. Both need to be optimized synchronously and dynamically adapted. Determining the angle parameter in isolation from the radial proportional parameter will cause the angle design to lose spatial support, failing to achieve its function of controlling flow and preventing dust accumulation; optimizing only the radial proportional parameter while ignoring the angle parameter will also lead to turbulent flow due to uncontrolled airflow direction. Only by coordinating and adjusting both as a whole can a suitable flow channel space and guidance mechanism be constructed to achieve optimal flow conditions and completely suppress dust accumulation.

[0075] Specifically, Its core function is to ensure that the airflow enters smoothly along the blade inlet, and its appropriate value needs to be determined based on... / Based on: If / A ratio that is too small (the inlet radius is too narrow relative to the reference radius) means that the radial space for airflow at the inlet is limited. If designed at a large angle, it can easily cause airflow to impact and separate within a narrow space, forming a vortex region; if / The ratio is too large (the inlet radius is too wide). If the angle is small, it may cause the airflow to disperse within the wide inlet space, reducing flow velocity stability. Only by combining... / Determined inlet radial dimensions, matching Only by adjusting the angle can the airflow enter in the optimal direction within the suitable radial space, avoiding inlet vortex and dust settling.

[0076] for (Projection exit angle) and / Both factors together determine the "diffraction efficiency and velocity distribution" at the blade outlet: The direction of the airflow outlet and the efficiency of kinetic energy conversion are controlled by angle design. / Then define the outlet radial range — if / The ratio is unreasonable (such as the outlet radius is too large relative to the reference radius), even if Designed as the optimal angle, it may cause excessive diffusion of airflow due to the excessive radial space of the outlet, weakening the diffusion effect and forming a negative pressure vortex area; if / Too small, Need a larger angle design to meet the design parameters, and a large angle is prone to airflow separation, causing airflow congestion and exacerbating flow rate changes. Only by optimizing / To the appropriate radial ratio, and adjusting the angle of Can make the airflow achieve efficient diffusion at the outlet while maintaining a smooth flow rate, avoiding dust adhesion and deposition.

[0077] In summary, / , / And , Are interrelated parameter systems: the radial ratio parameter provides a "space boundary" for the angle parameter, and the angle parameter provides "direction and path guidance" for the airflow in the radial space. Adjusting both as a whole can create an adaptive flow channel space and guidance mechanism to achieve optimal flow conditions and completely suppress dust accumulation.

[0078] In addition, the wrap angle Has an advantage in extending the "airflow guidance path" and optimizing the stability of the entire flow channel. The larger the blade wrap angle The longer the circular path of the airflow moving in the inter-blade passage, and the more sufficient the "guidance and work time" of the blade to the airflow. A short wrap angle ( Too small) will cause the airflow to "pass quickly" in the flow channel, and the blade will not be able to fully comb the airflow, making it prone to form local vortexes due to insufficient airflow movement; a reasonable large Can make the airflow gradually adapt to the blade profile changes in the flow channel, avoiding airflow turbulence caused by a short movement path, reducing vortex areas in the flow channel (especially in the middle region of the blade), and reducing the probability of dust adhesion in the flow channel. The size directly affects the distribution density of the blades in the circumferential direction (under the same impeller diameter, The larger the wrap angle, the fewer the number of blades; The smaller the wrap angle, the more the number of blades) — if Too large, the number of blades is too large, and the distance between the blades is too narrow, making the airflow prone to congestion in the flow channel, with sudden increases and decreases in flow rate, forming local vortexes and dust deposition, which cannot meet the design parameters; if Too small, too few number of blades, too wide blade spacing, airflow filling degree is insufficient, airflow is easy to disperse flow, forming a small vortex. Reasonable ∅ can balance the blade spacing and the flow passage section, ensure the airflow in the flow passage uniform, stable flow, no obvious congestion or dispersion, reduce dust deposition.

[0079] On this basis, Play an indirect role in preventing dust accumulation, The core role is to control the circumferential position difference of the projection of the adjacent flow channel line outlet, indirectly control the inclination angle of the blade in each small flow channel, and control the normal direction of the blade surface. If All are 0, the blade outlet edge is located on the same axial section, the blade outlet part is not twisted, similar to a two-dimensional blade, suitable for the case where the front and rear disc outlet parts are perpendicular to the axis and the two discs are parallel, and the adaptation ability is poor for non-parallel front and rear discs; if Too large, the inclination of the blade relative to the front and rear discs increases, the perpendicularity deteriorates, forming a rhombus-shaped flow passage, the wet circumference increases, the friction loss increases, and the through-flow capacity decreases. Inappropriate misalignment angles will cause uneven distribution of airflow at the outlet of each flow channel in the circumferential direction - the outlet spacing of some areas is too narrow, the airflow is congested, and the flow rate increases suddenly; the spacing of some areas is too wide, the airflow is dispersed, and the flow rate decreases suddenly, forming a "circumferential bias flow vortex area". This vortex area will attract dust particles, especially in the junction area of the impeller outlet and the non-volute structure, the circumferential bias flow will intensify the airflow turbulence, leading to dust deposition at the junction. When When designed reasonably, a square or nearly circular flow passage is formed, the circumferential friction loss is reduced, the flow capacity is increased, the airflow at the outlet of each flow channel is uniformly distributed in the circumferential direction, and there is no obvious bias flow, which can help And Optimize the outlet flow field and reduce dust accumulation caused by circumferential unevenness.

[0080] Under normal circumstances, the person skilled in the art will usually fall into the "single target priority" inertial thinking when designing the impeller parameters of the rail transit non-volute fan - when designing , the only goal is to reduce the inlet pressure loss, and the same angle is usually used, ignoring the adaptability of the airflow incoming direction and the blade inlet profile, leading to the formation of an inlet vortex area; when designing , in order to pursue "high wind speed output", a larger angle is usually used, which can increase the outlet flow rate, but intensifies the flow rate jump and negative pressure vortex, increasing the risk of dust accumulation; when designing , due to the limitation of "compact space layout", a smaller wrap angle is usually selected to adapt to the fan installation size by reducing the blade circumferential space, but the vortex flow in the flow channel is caused due to the short airflow guiding path; and the present application breaks these ideas and designs When the "airflow direction adaptation" is the core, the angle is determined by matching the airflow direction guided by the flow channel of the neck section of the air inlet, rather than single pursuit of minimum pressure loss, so as to eliminate the inlet vortex zone from the root When the "large angle and high wind speed" thinking is abandoned, a moderate acute angle is adopted to ensure a certain wind speed while improving the diffuser capacity, so as to avoid flow rate mutation and negative pressure vortex zone; the design When the "small space and small angle" limitation is broken, a larger wrap angle is adopted to optimize the airflow stability in the flow channel by prolonging the airflow guiding path, although part of the circumferential space is occupied, the vortex is greatly reduced; all these settings break the conventional cognition of the skilled in the art and have significant non-obviousness.

[0081] The flow channel of the air inlet 10 and the geometric parameters of the impeller are optimized and designed, so that the over-flow passage formed by the front disc 2 and the rear disc 3 of the impeller has strong diffuser capacity, strong power, smooth flow rate change, no mutation, reduced vortex zone formation, reduced outlet acceleration, low noise, and strong particle carrying capacity in the blade area, so as to fundamentally change the problems of serious dust accumulation, low running efficiency and the like.

[0082] In some preferred embodiments, the outlet edge diameter of the front blade root is The ratio of the outlet edge diameter of the front blade root to the outlet outer diameter D05 of the front disc 2 is 0.48-0.493. This setting limits the relative position of the blade between the front disc and the rear disc, and reserves space for blade welding and other processing techniques. If the ratio is too small, the overall size of the impeller and the overall size of the machine are increased, which does not meet the concept of "compact structure and small quality"; if the overall size of the impeller is increased, or the distance to the mounting bracket is too close, the dynamic and static interference disturbance is greatly increased, which does not meet the concept of "high efficiency and low noise". If the ratio is 0.5, the blade edge has no process forming amount, the forming is difficult, and the strength is weakened. If the ratio is greater than 0.5, the blade extends out of the front disc and the rear disc, the accident risk is increased, the blade power is weakened without the constraint of the front disc.

[0083] In some preferred embodiments, the number of the three-dimensional flow blades 4 is 7-15, preferably 9. If the number of blades is too small, the total power of the impeller is reduced, the diameter and the outlet angle need to be increased to compensate for the design requirements, and large angles are prone to flow separation, which hides the risk of dust accumulation, and large diameters have poor market competitiveness; if the number of blades is too large, the contact area between the airflow and the blade increases, the dust increases, and the flow channel is prone to blockage, and the effective working area of the fan is reduced.

[0084] In order to further optimize the flow field and anti-dust accumulation effect of the three-dimensional flow blade 4, a plurality of serrations 41 (as shown in FIG. 10) are additionally arranged at the outlet edge of the three-dimensional flow blade 4, and the overlapping parameters of the impeller and the air inlet 10 are optimized, and the specific design and function are as follows:

[0085] The serrations 41 of the outlet edge of the three-dimensional flow blade 4 need to meet specific size ratios: the length of the serrations 41 is 1 / 3 of the length of the outlet edge of the three-dimensional flow blade 4, and the length of the outlet edge of the three-dimensional flow blade 4 is 1 / 3 of the length of the impeller front disc 2. The length of the serrations 41 is 1 / 3 of the length of the outlet edge of the three-dimensional flow blade 4. The length of the serrations 41 is 1 / 3 of the length of the outlet edge of the three-dimensional flow blade 4. The length of the serrations 41 is 1 / 3 of the length of the outlet edge of the three-dimensional flow blade 4. The length of the serrations 41 is 1 / 3 of the length of the outlet edge of the three-dimensional flow blade 4. The length of the serrations 41 is 1 / 3 of the length of the outlet edge of the three-dimensional flow blade 4. The length of the serrations 41 is 1 / 3 of the length of the outlet edge of the three-dimensional flow blade 4.

[0086] The core role of this design is to change the airflow pattern at the tail of the blade and inhibit dust accumulation from the root of the flow field: the tail of the blade is a high-risk area of negative pressure vortex (a heavy dust accumulation area), and the serration structure can "cut" the large-area stable vortex at the tail into small-range and easily-dissipating micro-vortexes, destroy the flow field conditions for the continuous adhesion of dust particles, and avoid dust accumulation on the surface of the blade; at the same time, the serration design will not significantly increase the wind resistance, but can comb the flow state of the outlet airflow, reduce the airflow separation loss, and slightly improve the static pressure efficiency of the fan.

[0087] In some preferred embodiments, the overlap depth of the impeller and the air inlet 10 is 5-10 mm, and the overlap gap is 1-4 mm. The overlap depth refers to the axial length of the overlap of the impeller (specifically, the edge region of the impeller front disc close to the air inlet) and the air inlet (the air outlet end of the neck section of the air inlet) in the direction of the fan rotation axis (Z axis, with the airflow flowing from the negative direction of the Z axis to the positive direction). The overlap gap refers to the minimum gap width between the impeller (usually the edge of the impeller front disc) and the air inlet (the inner wall of the neck section of the air inlet) in the radial direction (i.e., the circumferential direction) perpendicular to the Z axis. The overlap depth and the overlap gap are the "core matching parameters" of the assembly of the impeller and the air inlet: the overlap depth determines the axial overlap range, ensuring "no leakage and stable transition" of the airflow; and the overlap gap controls the size of the radial gap, ensuring "no friction and less vortex". The two work together to ensure smooth flow in the connection area of the air inlet and the impeller, avoiding the efficiency loss caused by airflow leakage and reducing the dust accumulation problem caused by gap vortexes, laying a foundation for subsequent blade micro-vortex and dust accumulation prevention designs.

[0088] Through the above optimization design, the length of the serrations 41 is 1 / 3 of the length of the outlet edge of the three-dimensional flow blade 4, Figure 11a , Figure 11bAs shown, after the modification, the airflow separation phenomenon at the back of the three-dimensional flow blade 4 near the impeller front disc 2 completely disappears, the backflow area is hardly detectable, the velocity variation gradient between the two blades is gentle, the flow field distribution is uniform, the airflow velocity is significantly improved, and the ability to carry dust particles is greatly enhanced, thereby verifying the anti-dust and flow control effects from the flow field level.

[0089] The following optimized effects are obtained from the performance test and sand test results:

[0090] Under the same test conditions, the dust accumulation amount is reduced from 709 grams to 99 grams, with a dust accumulation reduction rate of 86%, significantly reducing the damage of dust adhesion to the fan; the power consumption is reduced by 15.6%, the energy loss is significantly reduced; the static pressure efficiency is increased by 7.8%, the airflow energy conversion efficiency is improved; the aerodynamic noise is reduced by 2.4 dB, and the noise pollution is effectively controlled. Therefore, the beneficial effects of reducing energy consumption, greatly reducing maintenance cost, prolonging the service life of the fan, and reducing noise pollution are achieved.

[0091] In summary, through the design of the sawtooth at the outlet of the blade and the optimization of the overlap parameters of the impeller and the air inlet, the present application achieves the multiple goals of "anti-dust, energy saving, efficiency improvement, and noise reduction", and ultimately achieves the beneficial effects of reducing equipment maintenance cost, prolonging the service life of the fan, and improving the reliability of the rail transit ventilation system.

[0092] In some preferred embodiments, as shown in Figure 12 As shown, the air inlet 10 is composed of an air inlet flange 101 and an air inlet neck segment 102, and along the circumferential direction of the air inlet flange 101, there are arrayed axial through holes 103 and 104, the small-diameter through holes 104 are used to realize the connection of the air inlet insulation plate 13 and the air inlet 10, and the large-diameter through holes 103 are used to avoid the connection components on the air inlet insulation plate 13 and to avoid the contact of the connection components on the flange, correspondingly, the air inlet mounting panel 1 is also provided with large-diameter through holes 103 to avoid the contact of the connection components with the air inlet mounting panel 1, and to ensure the insulation effect.

[0093] In some preferred embodiments, as shown in Figure 1 , Figure 2 As shown, the volute-free fan further comprises a motor connecting bracket 7, a panel reinforcing frame 9, a panel sealing gasket 14, a panel insulation pad 15, and a connecting piece 16, the motor 6 is installed on one side of the fan mounting panel 8 through the motor connecting bracket 7 and the connecting piece 16, and the motor 6 and the fan mounting panel 8 are connected and matched with the panel insulation pad 15 clamped therebetween, and the fan mounting panel 8 is integrated with the panel reinforcing frame 9 and the panel sealing gasket 14, for improving the structural strength and sealing performance.

[0094] In some preferred embodiments, the voluteless fan further comprises an air inlet sealing pad 12 and an air inlet insulation plate 13, the air inlet 10 is integrated on the air inlet mounting surface, the air inlet mounting surface plate 1 is provided with an air inlet sealing pad 12, the sealing surface of the air inlet 10 is arranged on the air inlet side of the air inlet mounting surface plate 1, and the air inlet mounting surface plate 1 is mounted on the air inlet insulation plate 13, thereby blocking the direct contact between the air inlet 10 and the air inlet mounting surface plate 1 through the air inlet insulation plate 13, so as to achieve the effect of insulation.

[0095] In some preferred embodiments, the air inlet mounting surface plate 1 and the fan mounting surface plate 8 are fixedly connected through an air inlet connecting support 11, and the air inlet connecting support 11 is arranged outside the impeller, so as to stably support the air inlet mounting surface plate 1 and the fan mounting surface plate 8, ensure the installation spacing and coaxiality between the two plates, and avoid deformation or relative displacement of the plates due to vibration; at the same time, the arrangement outside the impeller can avoid the core flow channel area around the impeller, does not interfere with the airflow, prevents vortex or airflow obstruction in the flow channel, and balances the structural stability and flow field smoothness.

[0096] In some preferred embodiments, the voluteless fan further comprises a shaft sleeve 5, the impeller is connected with the driving end (motor shaft) of the motor 6 through the shaft sleeve 5, so as to realize power transmission.

[0097] Through the air inlet insulation plate 13, the panel insulation pad 15 and the bolt insulation sleeve of the connecting piece 16, a multiple electrical isolation structure is formed, and the core function is to block the erosion of stray current and prevent the safety risk of motor leakage: in the rail transit system, the train running process will generate unexpected stray current (leakage current), and if the current directly contacts the metal parts of the fan (such as the air inlet 10, the impeller, the shell of the motor 6, etc.), it will cause electrochemical corrosion, which will greatly shorten the service life of the parts; the insulation parts can effectively block the conduction path of the stray current, so as to avoid the corrosion of the metal parts; at the same time, the insulation structure can realize electrical isolation, prevent the internal leakage of the motor 6 from being conducted to the rail or the vehicle body, so as to ensure the safety of passengers and avoid damage to other equipment of the rail transit system caused by leakage.

[0098] Embodiment 1

[0099] The ratio of the air inlet diameter D01 of the air inlet 10 to the air outlet diameter D02 of the air inlet 10 is set to 1.02, the minimum diameter of the air inlet 10 is the throat diameter D03, the ratio of the throat diameter D03 of the air inlet 10 to the air outlet diameter D02 of the air inlet 10 is set to 0.92, and the ratio of the throat height H02 to the air inlet height H01 is set to 0.35.

[0100] The impeller front disc 2 is composed of a front disc arc segment 201 and a front disc straight segment 202. The front disc arc segment 201 and the front disc straight segment 202 are tangent. The radius of the front disc arc segment 201 is 40mm, and the forming angle of the front disc straight segment 202 is... The inlet projection diameter D04 of the impeller front disc 2 is 0.65, and the ratio of the outlet outer diameter D05 of the impeller front disc 2 to the outlet outer diameter D05 of the impeller front disc 2 is 0.3 along the Z-axis direction.

[0101] In some preferred embodiments, along the Z-axis, the impeller rear disk 3 is composed of a first straight segment 301, a first arc segment 304, a second straight segment 302, and a second arc segment 303 connected in sequence. Both arc segments of the impeller rear disk 3 are tangent to their adjacent straight segments. The radius of the second arc segment 303 is 150mm; the radius of the first arc segment 304 is 10mm; and the forming angle of the second straight segment 302 is... The angle is 15°; the ratio of the center diameter D06 of the rear disc center hole of the impeller rear disc 3 to the outlet outer diameter D05 of the front disc outer edge of the impeller front disc 2 is 0.3; the ratio of the outer edge diameter D07 of the impeller rear disc 3 to the outlet outer diameter D05 of the front disc outer edge of the impeller front disc 2 is 1; the ratio of the height H06 of the impeller rear disc 3 to the height H07 of the impeller is 0.4. The ratio of the height H07 of the impeller to the outlet outer diameter D05 of the front disc outer edge of the impeller front disc 2 is 0.21.

[0102] The specific design parameters of the impeller are as follows:

[0103]

[0104] In this embodiment, the performance meets the design requirements, power consumption is reduced by 10%, and the flow field inside the impeller is as follows: Figure 13a As shown, near the front plate on the back of the blades, there is no backflow zone before the airflow exits the impeller, resulting in smooth overall flow. The velocity direction is consistent with the main flow direction, making it difficult for dust to settle. For example... Figure 13b As shown, near the impeller back plate, the airflow does not separate on the back of the blades from the moment it enters them, resulting in good flow and preventing large-scale deposition of sand and dust.

[0105] Example 2

[0106] The ratio of the air inlet diameter D01 to the air outlet diameter D02 of the air inlet 10 is set to 1.6. The minimum diameter of the air inlet 10 is the throat diameter D03. The ratio of the throat diameter D03 to the air outlet diameter D02 of the air inlet 10 is set to 0.95. The ratio of the throat height H02 to the air inlet height H01 is set to 0.5.

[0107] The impeller front disc 2 is composed of a front disc arc segment 201 and a front disc straight segment 202, the front disc arc segment 201 and the front disc straight segment 202 are tangent, the radius of the front disc arc segment 201 is 80 mm, the forming angle of the front disc straight segment 202 is 25°, the ratio of the inlet projection diameter D04 of the impeller front disc 2 to the outlet outer diameter D05 of the impeller front disc 2 is 0.8, and the ratio of the height H05 of the impeller front disc 2 to the height H07 of the impeller is 0.6 along the Z-axis direction.

[0108] In some preferred embodiments, along the Z-axis direction, the impeller rear disc 3 is composed of a rear disc first straight segment 301, a rear disc first arc segment 304, a rear disc second straight segment 302 and a rear disc second arc segment 303 connected in sequence, and the two arc segments of the impeller rear disc 3 are tangent to the straight segments adjacent thereto. The radius of the rear disc second arc segment 303 is 450 mm; the radius of the rear disc first arc segment 304 is 50 mm; the forming angle of the rear disc second straight segment 302 is 35°; the ratio of the center diameter D06 of the rear disc center hole end of the impeller rear disc 3 to the outlet outer diameter D05 of the front disc outer edge of the impeller front disc 2 is 0.5; the ratio of the rear disc outer edge diameter D07 of the impeller rear disc 3 to the outlet outer diameter D05 of the front disc outer edge of the impeller front disc 2 is 0.8; and the ratio of the height H06 of the impeller rear disc 3 to the height H07 of the impeller is 0.75. The ratio of the height H07 of the impeller to the outlet outer diameter D05 of the front disc outer edge of the impeller front disc 2 is 0.35.

[0109] The specific design of the impeller is as follows

[0110]

[0111] In this embodiment, the performance meets the design requirements, the power consumption is reduced by 9%, the flow field in the impeller is as shown in the figure, the airflow flows out of the impeller without backflow area near the back of the blade close to the front disc, the overall flow is stable, the speed direction is consistent with the main flow direction, and the sand and dust are difficult to deposit. As shown in the figure, close to the rear disc of the impeller, the airflow starts from entering the blade, no flow separation occurs on the back of the blade, the flow state is good, and the sand and dust cannot be deposited in a large area. Figure 14a Figure 14b

[0112] Comparative example

[0113] In some embodiments, the air inlet and the front disc shape line adopt parameters within the preferred range, and different rear discs and blades are adopted.

[0114] ​​​​Along the Z-axis, the impeller rear disk 3 is composed of a first straight segment 301, a first arc segment 304, a second straight segment 302, a second arc segment 303, and a third straight segment tangent to them, connected in sequence. Both arc segments of the impeller rear disk 3 are tangent to their adjacent straight segments. The radius of the second arc segment 303 is 21 mm; the radius of the first arc segment 304 is 21 mm; the forming angle of the second straight segment 302 is... The angle is 64.7°; the ratio of the center diameter D06 of the rear disc center hole of the impeller rear disc 3 to the outlet outer diameter D05 of the front disc outer edge of the impeller front disc 2 is 0.21; the ratio of the outer edge diameter D07 of the impeller rear disc 3 to the outlet outer diameter D05 of the front disc outer edge of the impeller front disc 2 is 0.99; the ratio of the height H06 of the impeller rear disc 3 to the height H07 of the impeller is 0.69. The ratio of the height H07 of the impeller to the outlet outer diameter D05 of the front disc outer edge of the impeller front disc 2 is 0.28. The main parameter of the rear disc is the forming angle. The diameter D06 is not within the preferred parameter range.

[0115] The specific design parameters of the impeller are as follows:

[0116]

[0117] In this embodiment, the fan performance meets the design requirements, but the efficiency is low, the power consumption is high, and the flow field inside the impeller is as follows: Figure 15a As shown, near the front disk on the back of the blade, a large area of ​​backflow occurs before the airflow exits the impeller. In this area, the gas flow is turbulent, the velocity suddenly decreases, and the velocity direction is inconsistent with the main flow direction, making it a major area for dust deposition. Figure 15b As shown, near the impeller back plate, the airflow begins to separate on the back of the blade from the moment it enters the blade. The separation occurs on the back of the blade, which accounts for about 2 / 3 of the total blade length. The velocity in this area is low, and the dust-carrying capacity is insufficient, so sand and dust are deposited here.

[0118] The specific embodiments of this application have been described in detail above. For those skilled in the art, several improvements and modifications can be made to this application without departing from the principle of this application, and these improvements and modifications also fall within the protection scope of the claims of this application.

Claims

1. A kind of impeller, including impeller front disc (2), impeller rear disc (3) and several ternary flow blades (4) connected between the impeller front disc (2) and the impeller rear disc (3), it is characterized in that: In the direction of Z axis, the space between the two profile lines of the impeller front disc (2) and the impeller rear disc (3) is equally divided into four small flow channels with equal volume, forming five different small flow channel lines, respectively marked as a, b, c, d, e, wherein a is the front disc profile line, and e is the rear disc profile line, and the intersection line of the five lines with the same three-dimensional flow blade (4) is 、 、 、 、 , 、 、 、 、 The projection lines i on the cross section perpendicular to the Z axis are respectively marked as 、 、 、 、 ; Specific design parameter range is as follows: The curved surface, where the three-element flow blade (4) is connected with the front disc (2) of the impeller, is a front blade root, and the diameter of the outlet edge of the front blade root is the blade outlet edge diameter The straight-line distance between the end point of the outlet edge and the center of the rotating shaft of the fan is the outlet projection diameter The distance between the inlet edge end point of the i-th projection line and the projection axis center is the inlet projection diameter The angle between the tangent of the inlet edge end point of the i-th projection line and the tangent of the circular arc between the end point and the projection axis center is the projection inlet angle The angle between the tangent of the outlet edge end point of the i-th projection line and the tangent of the circular arc between the end point and the projection axis center is the projection outlet angle ; The impeller front disc (2) is composed of a tangent front disc arc segment (201) and a front disc straight segment (202), wherein the forming angle of the front disc straight segment (202) is... The range is 0°-25°. The ratio of the inlet projection diameter D04 of the impeller front plate (2) to the outlet outer diameter D05 of the impeller front plate (2) is 0.65-0.

8. Along the Z-axis direction, the ratio of the height H05 of the impeller front plate (2) to the height H07 of the impeller is 0.3-0.

6. The impeller back disc (3) is composed of sequentially connected back disc first linear segment (301), back disc first arc segment (304), back disc second linear segment (302), back disc second arc segment (303), the forming angle of the back disc second linear segment (302) is in the range of 15°-35°. the range of 15°-35°. The ratio of the center diameter D06 of the rear disc center hole end of the impeller rear disc (3) and the outlet outer diameter D05 of the front disc outer edge of the impeller front disc (2) is 0.3-0.5;The ratio of the rear disc outer edge diameter D07 of the impeller rear disc (3) and the outlet outer diameter D05 of the front disc outer edge of the impeller front disc (2) is 0.8-1;The ratio of the height H06 of the impeller rear disc (3) and the height H07 of the impeller is 0.4-0.75; The ratio of the height H07 of the impeller and the outlet outer diameter D05 of the front disc outer edge of the impeller front disc (2) is 0.21-0.

35.

2. The impeller according to claim 1, characterized in that: Along the airflow direction from the inlet to the outlet, the angle between the circumferential angle difference formed by the i-th projection line and its adjacent projection line at the corresponding radii on the outlet side is the misalignment angle. , , , , Misalignment angle The design parameter range is 0-6, 0-5, 0-4, 0-3.

3. The impeller according to claim 1, characterized in that: The curved surface of the three-dimensional flow blade (4) connected with the front disc (2) of the impeller is a front blade root, and the outlet edge diameter of the front blade root is The ratio of the outlet edge diameter of the front blade root to the outlet outer diameter D05 of the front disc (2) of the impeller is 0.48-0.

493.

4. The impeller according to claim 1, characterized in that: The number of the ternary flow blades (4) is 7-15.

5. The impeller according to claim 1, characterized in that: The exit edge of the three-dimensional flow blade (4) is provided with several serrations (41) to... This indicates the length of the exit edge of the three-dimensional flow blade (4). The spacing between two adjacent saw teeth (41) is specified, wherein there are no saw teeth in one-third of the area near the outlet edge of the impeller front disc (2), and the saw teeth (41) are arranged only in the remaining two-thirds of the area, and the spacing between two adjacent saw teeth (41) is specified. The length of the outlet edge of the three-dimensional flow blade (4) The ratio ranges from 0.11 to 0.

15.

6. A voluteless fan, including the impeller according to any one of claims 1 to 5, and further including an air inlet mounting panel (1) connected along a vertical rotation axis Z axis direction, a motor (6), a fan mounting panel (8), it is characterized in that: The air inlet mounting panel (1) is provided with an air inlet (10), and the air inlet (10) is connected with one end of the impeller, to form a gradually expanding air flow passage; The air inlet (10) includes an air inlet neck segment (102), and the air inlet neck segment (102) is composed of a circular arc segment (105) and a straight line segment (106), and the straight line segment (106) is tangent to the circular arc segment (105); Wherein, the ratio of the air inlet diameter D01 of the air inlet (10) and the air outlet diameter D02 of the air inlet (10) is 1.02-1.

6.

7. The voluteless fan according to claim 6, characterized in that: The minimum diameter of the air inlet (10) is throat diameter D03, and the ratio of the throat diameter D03 of the air inlet (10) and the air outlet diameter D02 of the air inlet (10) is 0.92-0.95, and the ratio of the throat height H02 and the air inlet height H01 is 0.35-0.

5.

8. The voluteless fan according to claim 6, characterized in that: The overlap depth of the impeller front disc (2) and the air inlet (10) is 5-10mm, and the overlap gap is 1-4mm.

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