Multi-stage acting fan impeller

Abstract

The utility model discloses a multistage acting fan impeller which comprises a supporting assembly, a primary acting blade set and a secondary acting blade set. A plurality of inner blades of the primary acting blade set are distributed on the central supporting wall at intervals in the circumferential direction of the supporting assembly. A plurality of outer blades of the secondary acting blade set are distributed between the first annular wall and the second annular wall at intervals in the circumferential direction of the supporting assembly. The primary acting blade set is located in an acting area defined by the secondary acting blade set. All the inner blades rotate in the same direction, all the outer blades rotate in the same direction, and the rotating directions of the inner blades are opposite to those of the outer blades; the primary acting blade set on the inner side conducts primary acting, so that airflow is converted into the radial direction from the axial direction in advance, the airflow speed is remarkably increased within a short time, and therefore the larger airflow speed and the better airflow direction condition are provided for secondary acting, the capacity loss is small, and the total pressure efficiency of air outlet is high; and the air performance of the fan system is optimized.

Description

Technical Field

[0001] This utility model relates to the technical field of centrifugal fans, and in particular to a multi-stage power fan impeller. Background Technology

[0002] In existing technologies, impellers are mostly designed with a single-stage structure, and the blades are usually designed with a single bending direction in order to effectively accelerate and guide the airflow during rotation.

[0003] Patent No. CN219865582U: This utility model patent discloses an impeller for a dual-inlet centrifugal fan, a centrifugal fan, and a range hood. The impeller design includes front and rear discs and a middle disc. Blades are arranged circumferentially along the middle disc. A key feature is that the blade design reduces the difference in flow state on both sides of the impeller, minimizing secondary flow and thus improving fan performance and reducing noise. The blade design features a first blade profile comprising at least two arc segments connected sequentially from its first side to its second side, with the radius of curvature increasing sequentially. A second blade profile comprises at least three arc segments connected sequentially from its third side to its fourth side, with the radius of curvature increasing sequentially. The arc length of the first blade profile is less than the arc length of the second blade profile. Furthermore, at least one arc segment of the first blade at the air inlet end adjacent to the impeller overlaps with at least one arc segment of the second blade at the air inlet end adjacent to the impeller in the axial projection of the impeller.

[0004] In the impeller structure of the aforementioned patent, after the airflow enters vertically, it collides with the central disk and then turns before entering the airflow channel between the blades. Although the airflow is optimized by changing the shape and angle of the blades, the improvement in efficiency is not ideal, and the utilization rate of the blades is low. This not only reduces the working efficiency of the fan, but also increases noise and energy consumption. Utility Model Content

[0005] The technical problem to be solved by this utility model is to provide a two-stage fan impeller with higher total pressure efficiency and better air performance.

[0006] The technical solution adopted by this utility model to solve the above-mentioned technical problems is: a multi-stage working fan impeller, including a support assembly, a primary working blade group and a secondary working blade group;

[0007] The support assembly includes at least a first disk and a second disk arranged opposite to each other. The first disk is annular and includes a first annular wall. The second disk includes a second annular wall parallel to and opposite to the first annular wall and a central support wall.

[0008] The multiple inner blades of the primary working blade group are distributed at intervals along the circumference of the support assembly on the central support wall; the multiple outer blades of the secondary working blade group are distributed at intervals along the circumference of the support assembly between the first annular wall and the second annular wall.

[0009] The primary working blade group is located within the working area enclosed by the secondary working blade group; all the inner blades have the same rotation direction, all the outer blades have the same rotation direction, and the rotation direction of the inner blades is opposite to that of the outer blades.

[0010] The preferred technical solution adopted by this utility model to solve the above-mentioned technical problems is as follows: the inner blades extend axially and are evenly distributed along the circumference of the support assembly, and there is a primary airflow channel between two adjacent inner blades; the outer blades are evenly distributed along the circumference of the support assembly, and there is a secondary airflow channel between two adjacent outer blades; the minimum channel spacing of the primary airflow channel is greater than the maximum channel spacing of the secondary airflow channel.

[0011] The preferred technical solution adopted by this utility model to solve the above-mentioned technical problems is that the outer blade extension axis has an angle with the central axis and is inclined, thereby increasing the working area of ​​the blade at the same impeller height.

[0012] The preferred technical solution adopted by this utility model to solve the above-mentioned technical problems is as follows: the inner blade is inserted into the central support wall and reinforced by welding, and the extension axis of the inner blade is parallel to the central axis.

[0013] The preferred technical solution adopted by this utility model to solve the above-mentioned technical problems is: the channel spacing at the air inlet end of the primary airflow channel is less than or equal to the channel spacing at the air outlet end;

[0014] The channel spacing at the air inlet of the secondary airflow channel is greater than the channel spacing at the air outlet.

[0015] The preferred technical solution adopted by this utility model to solve the above-mentioned technical problem is: the end height of the primary working blade group is greater than or equal to half the height of the secondary working blade group, and less than the height of the secondary working blade group.

[0016] The end height refers to the maximum height of the inner blade of the primary working blade group within a working zone enclosed by the secondary working blade group.

[0017] The preferred technical solution adopted by this utility model to solve the above-mentioned technical problems is: a multi-stage working fan impeller, including a support assembly, a primary working blade group and a secondary working blade group;

[0018] The support assembly includes a first disk, a second disk, and a third disk in sequence. The first disk includes a first annular wall; the second disk includes a second annular wall and a central support wall; the first disk includes a third annular wall; and the first annular wall, the second annular wall, and the second annular wall are parallel to each other.

[0019] The multiple outer blades of the secondary working blade group are distributed circumferentially along the support assembly and pass through the second ring and are connected between the first annular wall and the third annular wall.

[0020] The area enclosed by the secondary working blade assembly is divided by the second disk. The part between the first disk and the second disk is called the first working area, and the part between the second disk and the third disk is called the second working area.

[0021] The multiple inner blades of the single-operation blade group are distributed at intervals along the circumference of the support assembly on the central support wall.

[0022] The central support wall is provided with an arc-shaped through hole, and the inner blade passes through the arc-shaped through hole into the central support wall, and is located in the first working area and the second working area respectively.

[0023] All the inner blades have the same rotation direction, all the outer blades have the same rotation direction, and the rotation direction of the inner blades is opposite to that of the outer blades.

[0024] The preferred technical solution adopted by this utility model to solve the above-mentioned technical problems is: the inner blades are evenly distributed along the circumference of the support assembly and have a primary airflow channel;

[0025] The outer blades are evenly distributed along the circumference of the support assembly and have a secondary airflow channel;

[0026] The channel spacing at the air inlet end of the primary airflow channel is less than or equal to the channel spacing at the air outlet end.

[0027] The channel spacing at the air inlet of the secondary airflow channel is greater than the channel spacing at the air outlet.

[0028] The minimum channel spacing of the primary airflow channel is greater than the maximum channel spacing of the secondary airflow channel.

[0029] The preferred technical solution adopted by this utility model to solve the above-mentioned technical problem is: the height distance between the first annular wall and the second annular wall is greater than the height distance between the second annular wall and the third annular wall;

[0030] The height of the inner blade located in the first working zone is greater than the height of the inner blade located in the second working zone.

[0031] The preferred technical solution adopted by this utility model to solve the above-mentioned technical problems is: the end faces of the inner blades in the first working area are located at the same height so as to be parallel to the first disk;

[0032] The end face of the inner blade in the second working area gradually tilts away from the second disk from the center to the outer periphery.

[0033] Compared with the prior art, the advantages of this utility model are: after the gas enters the impeller, the inner primary working blade group performs primary work, which causes the airflow to change from axial to radial in advance, and the airflow speed is significantly increased in a short time. This provides greater airflow speed and better airflow direction conditions for secondary work, resulting in low energy loss, high total pressure efficiency of the outlet air, and optimized air performance of the fan system. Attached Figure Description

[0034] The present invention will be further described in detail below with reference to the accompanying drawings and preferred embodiments. However, those skilled in the art will understand that these drawings are drawn only for the purpose of explaining the preferred embodiments and therefore should not be construed as limiting the scope of the present invention. Furthermore, unless specifically indicated, the drawings are only schematic representations of the composition or structure of the described objects and may contain exaggerated depictions, and the drawings are not necessarily drawn to scale.

[0035] Figure 1 This is a schematic diagram of the multi-stage power fan impeller in Example 1. Figure 1 ;

[0036] Figure 2 This is a schematic diagram of the multi-stage power fan impeller in Example 1. Figure 2 ;

[0037] Figure 3 This is a schematic diagram of the multi-stage power fan impeller in Example 2. Figure 1 ;

[0038] Figure 4 This is a schematic diagram of the multi-stage power fan impeller in Example 2. Figure 2 ;

[0039] Figure 5 This is a schematic diagram of the multi-stage power fan impeller in Example 2. Figure 3 ;

[0040] Figure 6 This is an exploded view of the multi-stage power fan impeller in Example 2. Detailed Implementation

[0041] The preferred embodiments of the present invention will now be described in detail with reference to the accompanying drawings. Those skilled in the art will appreciate that these descriptions are merely descriptive and exemplary and should not be construed as limiting the scope of protection of the present invention.

[0042] It should be noted that similar labels in the following figures indicate similar items; therefore, once an item is defined in one figure, it will not be further defined and explained in subsequent figures.

[0043] In the description of this utility model, it should be noted that the terms "upper," "lower," "front," "rear," "left," "right," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, or the orientation or positional relationship commonly used when the product of this utility model is in use. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model. Similarly, "first" and "second" are only for ease of understanding and have no other directional meaning, and cannot be considered as limitations on this utility model.

[0044] Example 1:

[0045] like Figure 1 , 2 As shown, this embodiment provides a multi-stage working impeller for a centrifugal fan with single-sided air intake. The impeller includes a support assembly 10, a primary working blade assembly 20, and a secondary working blade assembly 30.

[0046] like Figure 1 As shown, the support assembly 10 includes a first disk 11 and a second disk 12 arranged opposite to each other. The first disk 11 is annular and includes a first annular wall a. The second disk 12 includes a second annular wall b parallel to and opposite to the first annular wall a and a central support wall c. Multiple outer blades 301 of the secondary working blade assembly 30 are spaced apart circumferentially between the first annular wall a and the second annular wall b of the support assembly 10. A shaft hole d is provided in the middle of the central support wall c, through which the motor passes. The inner hole of the first disk 11 is the air inlet of the entire fan impeller. The secondary working blade assembly 30 and the central support wall c enclose a working area, within which the primary working blade assembly 20 is located. Multiple inner blades 201 of the primary working blade assembly 20 are spaced apart circumferentially on the central support wall c of the support assembly 10. The annular structures formed by the primary working blade assembly 20 and the secondary working blade assembly 30 are coaxial. All inner blades 201 have the same rotation direction, all outer blades 301 have the same rotation direction, and the rotation direction of the inner blades 201 is opposite to that of the outer blades 301.

[0047] After the gas enters the impeller, the inner primary working blade assembly 20 performs primary work, causing the airflow to change from axial to radial direction ahead of time, and significantly increasing the airflow velocity in a short period of time. This provides greater airflow velocity and better airflow direction conditions for secondary work. During secondary work, the secondary working blade assembly 30, due to the high initial airflow velocity and high radial direction, has low energy loss, high total pressure efficiency of the outlet air, and optimizes the air performance of the fan system.

[0048] The inner and outer blades 301 rotate in opposite directions, so that the airflow after one work is "caught" by the secondary work blade group 30 after flowing out of the primary work blade group 20. This reduces the turbulence and dispersion of the airflow, allowing more airflow to reach the working area of ​​the secondary work blade group 30, thereby improving the pressurization effect of the fan system.

[0049] Furthermore, it should be noted that in the original structure, because the axial airflow first impacts the central support wall c, and then rebounds from the central support wall c, it turns to form airflows with different directions that enter between the blades. Therefore, the airflow is generally close to the central support wall c, and the outer part of the blades away from the second disk 12 has a low utilization rate, thus affecting the work efficiency. In this embodiment, however, by performing work through the blade assembly 20 in a single operation, the height of the airflow is increased, thereby making more efficient use of the outer part of the blades away from the central support wall c, and greatly improving the total pressure efficiency.

[0050] Through two-stage efficiency enhancement, the aerodynamic performance of fans of the same size is improved. Under the same power requirements, producers can reduce fan size, thereby lowering production costs, saving resources, and realizing industrial economic benefits.

[0051] like Figure 1 , 2 As shown, the extension axis of the inner blade 201 is parallel to the central axis, which facilitates the work done on the axial airflow. The extension axis of the outer blade 301 is inclined at an angle to the central axis, thereby increasing the working area of ​​the blade at the same impeller height and improving the working efficiency.

[0052] like Figure 1 As shown, the inner blades 201 extend axially and are evenly distributed circumferentially along the support assembly 10, with a primary airflow channel S1 between adjacent inner blades 201. The outer blades 301 are evenly distributed circumferentially along the support assembly 10, with a secondary airflow channel S2 between adjacent outer blades 301. The minimum channel spacing of the primary airflow channel S1 is greater than the maximum channel spacing of the secondary airflow channel S2. The circumferentially distributed inner and outer blades 301 make the airflow more uniform, reduce airflow losses caused by airflow turbulence, and improve the aerodynamic performance of the fan.

[0053] As shown in Figure 1, the channel spacing at the inlet end of the primary airflow channel S1 is less than or equal to the channel spacing at the outlet end. The channel spacing gradually increases from the inside to the outside, allowing the axial airflow to be more tightly captured by the inner blades 201, reducing the possibility of airflow escape, improving airflow capture efficiency, making it easier to accelerate the airflow, thereby improving the efficiency of the fan, and also helping to reduce the impact loss of the airflow when entering the impeller.

[0054] like Figure 1As shown, the channel spacing at the air inlet of the secondary airflow channel S2 is greater than that at the air outlet, so the fluid velocity can always be in an accelerated state, which is beneficial to reduce the airflow separation on the suction surface, reduce the vortex area in the air duct, and thus improve the impeller working efficiency.

[0055] like Figure 2 As shown, the end height of the primary working blade group 20 is greater than or equal to half the height of the secondary working blade group 30, but less than the height of the secondary working blade group 30. The end height refers to the maximum height of the inner blade 201 of the primary working blade group 20 within a working area enclosed by the secondary working blade group 30. This height setting increases the working area, enabling more effective acceleration and lifting of the airflow, thus improving the overall utilization rate of the blades in the secondary working blade group 30. By optimizing the layout and height of the inner blade 201 in the forward working area, the aerodynamic performance of the entire fan system is significantly improved. This design not only enhances the total pressure capacity of the fan but also promotes smooth airflow throughout the entire fan system, reducing energy loss.

[0056] like Figure 2 As shown, the inner blade 201 is inserted into the central support wall c and reinforced by welding. The insertion strengthens the connection of the inner blade 201, and the blade is limited in the direction perpendicular to the axial direction to achieve fixation in one direction, and then further fixation in the axial direction is achieved by welding.

[0057] Example 2:

[0058] like Figure 3-4 As shown, this embodiment provides a multi-stage working impeller for a centrifugal fan with dual-sided air intake. The impeller includes a support assembly 10', a primary working blade assembly 20', and a secondary working blade assembly 30'.

[0059] like Figure 3-5As shown, the support assembly 10' sequentially includes a first disk 11', a second disk 12', and a third disk 13'. The first disk 11' includes a first annular wall a'. The second disk 12' includes a second annular wall b' and a central support wall c'. The first disk 11' includes a third annular wall d'. The first annular wall a', the second annular wall b', and the third annular wall d' are parallel and opposite to each other. Multiple outer blades 301' of the secondary work blade assembly 30' are distributed circumferentially along the support assembly 10' and pass through the second annular ring, connecting between the first annular wall a' and the third annular wall d'. The area enclosed by the secondary work blade assembly 30' is divided by the second disk 12'. The portion between the first disk 11' and the second disk 12' is designated as the first work area, and the portion between the second disk 12' and the third disk 13' is designated as the second work area. Multiple inner blades 201' of the primary work blade assembly 20' are distributed circumferentially along the support assembly 10' on the central support wall c'. An arc-shaped through hole is provided on the central support wall c'. The inner blade 201' passes through the central support wall c' through the arc-shaped through hole and is located in the first working zone and the second working zone respectively. All inner blades 201' have the same rotation direction, and all outer blades 301' have the same rotation direction. The rotation direction of the inner blades 201' is opposite to that of the outer blades 301'.

[0060] After the gas enters the impeller, the inner primary working blade assembly 20' performs primary work, causing the airflow to change from axial to radial direction earlier and significantly increasing the airflow velocity in a short time. This provides greater airflow velocity and better airflow direction conditions for secondary work. During secondary work, the secondary working blade assembly 30' has low energy loss and high total pressure efficiency due to its high initial airflow velocity and high radial direction, thus optimizing the aerodynamic performance of the fan system.

[0061] The inner and outer blades 301' rotate in opposite directions, so that the airflow after the first work is "caught" by the second work blade group 30' after it flows out from the first work blade group 20'. This reduces the turbulence and dissipation of the airflow, allowing more airflow to reach the work area of ​​the second work blade group 30', thereby improving the pressurization effect of the fan system.

[0062] Furthermore, it should be noted that in the original structure, because the axial airflow first impacts the central support wall c', and then rebounds from the central support wall c', it turns to form airflows with different directions that enter between the blades. Therefore, the airflow is generally close to the central support wall c', and the outer part of the blades far from the second disk 12' has a low utilization rate, thus affecting the work efficiency. In this embodiment, however, by performing work with the blade assembly 20' in a single operation, the height of the airflow is increased, thereby making more efficient use of the outer part of the blades far from the central support wall c' and greatly improving the total pressure efficiency.

[0063] Through two-stage efficiency enhancement, the aerodynamic performance of fans of the same size is improved. Under the same power requirements, producers can reduce fan size, thereby lowering production costs, saving resources, and realizing industrial economic benefits.

[0064] like Figure 6 As shown, the inner blades 201' are evenly distributed circumferentially along the support assembly 10', forming a primary airflow channel S1'. The outer blades 301' are evenly distributed circumferentially along the support assembly 10', forming a secondary airflow channel S2'. The channel spacing at the air inlet end of the primary airflow channel S1' is less than or equal to the channel spacing at the air outlet end. The channel spacing at the air inlet end of the secondary airflow channel S2' is greater than the channel spacing at the air outlet end. The minimum channel spacing of the primary airflow channel S1' is greater than the maximum channel spacing of the secondary airflow channel S2'.

[0065] like Figure 3-5 As shown, the height distance between the first annular wall a' and the second annular wall b' is greater than the height distance between the second annular wall b' and the third annular wall. The height of the inner blade 201' located in the first working zone is greater than the height of the inner blade 201' located in the second working zone. The motor is installed in the second working zone.

[0066] like Figure 3-5 As shown, the end faces of the inner blades 201' in the first working zone are at the same height and parallel to the first disk 11'. The end faces of the inner blades 201' in the second working zone gradually tilt away from the second disk 12' from the center outwards. The tilted design of the blade end faces allows for a larger blade surface area within a limited space, thereby maximizing the airflow contact area and working effect without interfering with the motor installation, and achieving axial lifting of the airflow.

[0067] like Figure 3-6 As shown, the inner blade 201' is inserted into the central support wall c' and the connection is reinforced by welding. The insertion arrangement strengthens the connection of the inner blade 201', and the blade is limited in the direction perpendicular to the axial direction to achieve fixation in one direction, and then further fixation in the axial direction is achieved by welding.

[0068] This invention introduces a multi-stage power fan impeller. Specific examples are used to illustrate the principle and implementation of this invention. The descriptions of the embodiments are merely for the purpose of helping to understand this invention and its core ideas. It should be noted that those skilled in the art can make various improvements and modifications to this invention without departing from its principles, and these improvements and modifications also fall within the protection scope of the claims of this invention.

Claims

1. A multi-stage power fan impeller, characterized in that: Includes support components, primary power blade assembly, and secondary power blade assembly; The support assembly includes at least a first disk and a second disk arranged opposite to each other. The first disk is annular and includes a first annular wall. The second disk includes a second annular wall parallel to and opposite to the first annular wall and a central support wall. The multiple inner blades of the primary working blade group are distributed at intervals along the circumference of the support assembly on the central support wall; the multiple outer blades of the secondary working blade group are distributed at intervals along the circumference of the support assembly between the first annular wall and the second annular wall. The primary working blade group is located within the working area enclosed by the secondary working blade group; all the inner blades have the same rotation direction, all the outer blades have the same rotation direction, and the rotation direction of the inner blades is opposite to that of the outer blades.

2. The multi-stage power fan impeller according to claim 1, characterized in that: The outer blade extension axis is inclined at an angle to the central axis, thereby increasing the working area of ​​the blade at the same impeller height.

3. The multi-stage power fan impeller according to claim 1, characterized in that: The inner blade is inserted into the central support wall and reinforced by welding. The extension axis of the inner blade is parallel to the central axis.

4. The multi-stage power fan impeller according to claim 1, characterized in that: The inner blades extend axially and are evenly distributed along the circumference of the support assembly, with a primary airflow channel between adjacent inner blades; the outer blades are evenly distributed along the circumference of the support assembly, with a secondary airflow channel between adjacent outer blades; the channel spacing at the air inlet end of the primary airflow channel is less than or equal to the channel spacing at the air outlet end; the channel spacing at the air inlet end of the secondary airflow channel is greater than the channel spacing at the air outlet end.

5. The multi-stage power fan impeller according to claim 1, characterized in that: The end height of the primary power blade group is greater than or equal to half the height of the secondary power blade group, and less than the height of the secondary power blade group. The end height refers to the maximum height of the inner blade of the primary working blade group within a working zone enclosed by the secondary working blade group.

6. A multi-stage power fan impeller, characterized in that: Includes support components, primary power blade assembly, and secondary power blade assembly; The support assembly includes a first disk, a second disk, and a third disk in sequence. The first disk includes a first annular wall; the second disk includes a second annular wall and a central support wall; the first disk includes a third annular wall; and the first annular wall, the second annular wall, and the second annular wall are parallel to each other. The multiple outer blades of the secondary working blade group are distributed circumferentially along the support assembly and pass through the second ring and are connected between the first annular wall and the third annular wall. The area enclosed by the secondary working blade assembly is divided by the second disk. The part between the first disk and the second disk is called the first working area, and the part between the second disk and the third disk is called the second working area. The multiple inner blades of the single-operation blade group are distributed at intervals along the circumference of the support assembly on the central support wall. The central support wall is provided with an arc-shaped through hole, and the inner blade passes through the arc-shaped through hole into the central support wall, and is located in the first working area and the second working area respectively. All the inner blades have the same rotation direction, all the outer blades have the same rotation direction, and the rotation direction of the inner blades is opposite to that of the outer blades.

7. The multi-stage power fan impeller according to claim 6, characterized in that: The height distance between the first annular wall and the second annular wall is greater than the height distance between the second annular wall and the third annular wall; The height of the inner blade located in the first working zone is greater than the height of the inner blade located in the second working zone.

8. The multi-stage power fan impeller according to any one of claims 6-7, characterized in that: The end faces of the inner blades in the first working zone are at the same height and parallel to the first disk; The end face of the inner blade in the second working zone gradually tilts away from the second disk from the center to the outer periphery.

Images