Impeller and fan
By setting guide vanes on the impeller blades, the axial force is counteracted by the reaction force, which solves the problem of ceramic bearing wear in high-speed centrifugal fans, extends bearing life, and improves impeller efficiency.
Patent Information
- Application Number
- CN202520408149.7
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Priority Date
- 2024-04-22
- Filing Date
- 2025-03-10
- Publication Date
- 2026-02-10
- Estimated Expiration
- 2035-03-10
AI Technical Summary
The axial force generated by the impeller of existing high-speed centrifugal fans cannot be effectively balanced, which leads to accelerated wear of ceramic bearings and reduced service life.
Inclined guide vanes are installed on the blades to generate a reaction force that counteracts or reduces the axial force when the impeller rotates. The design of the guide vanes creates a combined force on the ceramic bearing, reducing bearing wear.
The design of the guide vanes reduces wear on the ceramic bearings, extends their service life, and improves the impeller's working efficiency and rotational stability.
Smart Images
Figure CN223894515U_ABST
Abstract
Description
Technical Field
[0001] This utility model relates to the field of wind turbine equipment technology, and in particular to an impeller and a wind turbine. Background Technology
[0002] Centrifugal fans are machines that rely on input mechanical energy to increase gas pressure and discharge gas; they are a type of driven fluid machinery. Centrifugal fans are widely used in ventilation, dust removal, and cooling in factories, mines, tunnels, cooling towers, vehicles, ships, and buildings; for ventilation and induced draft in boilers and industrial furnaces; for cooling and ventilation in air conditioning equipment and household appliances; for grain drying and conveying; as a wind source in wind tunnels and for inflating and propelling hovercraft, etc.
[0003] The main components of a centrifugal fan include the volute, impeller, and motor. When the impeller rotates at high speed to intake air, the air inlet generates a reaction force opposite to the direction of air intake. This reaction force exerts an outward force on the motor shaft, i.e., an axial force. This axial force is transmitted to the bearings through the shaft, causing bearing wear and reducing service life.
[0004] In the existing technology, air-suspended centrifugal fans and magnetic levitation centrifugal fans generally need to be equipped with thrust bearings to balance the axial force generated by the impeller. However, for some high-speed centrifugal fans, because the ceramic bearings used are not compatible with the thrust bearings, the axial force generated by the impeller will be directly transmitted to the ceramic bearings through the motor shaft, resulting in accelerated wear of the ceramic bearings and reduced service life. Utility Model Content
[0005] In view of this, the present invention provides an impeller and a fan to solve the problem that some high-speed centrifugal fans in the prior art cannot well balance the axial force generated by the impeller, which easily leads to accelerated wear of ceramic bearings and reduced service life.
[0006] To achieve one or more of the above objectives or other objectives, this utility model proposes: an impeller, comprising: a hub, a rear cover plate and a plurality of blades, wherein the hub is coaxially disposed on the rear cover plate and the plurality of blades are evenly distributed on the rear cover plate around the axis of the hub;
[0007] The front end of the blade is close to the axis of the hub and flush with the circumference of the rear cover plate, the rear end of the blade is away from the axis of the hub, and the rear half of the blade is provided with a guide vane, which is inclined downward in the direction of rotation of the impeller.
[0008] Preferably, the guide vane is disposed on the outer edge of the blade, and the height from the rear side of the guide vane to the root of the blade is 1 mm higher than the height from the front side of the guide vane to the root of the blade.
[0009] Preferably, the guide vane has a plurality of guide grooves distributed on it, the depth of the guide grooves is 5mm, and the orientation of the guide grooves is the same as the rotation direction of the impeller.
[0010] Preferably, the top wall of the guide vane is a plane, the angle between the guide vane and the blade is 80°-89°, the two sides of the guide vane extend beyond the two side walls of the blade, and the width from the front side of the guide vane to the front side wall of the blade is greater than or equal to the width from the rear side of the guide vane to the rear side wall of the blade.
[0011] Preferably, the guide vane includes a front plate and a rear plate, the front side of the front plate extends out of the front sidewall of the blade in the direction of rotation of the impeller, and the rear side of the rear plate is flush with the rear sidewall of the blade.
[0012] Preferably, the angle between the front plate and the blade is 80°-89°, and the angle between the rear plate and the blade is 6° smaller than the angle between the front plate and the blade.
[0013] Preferably, the rear sidewall of the guide vane is integrally connected to the front sidewall of the blade, and the bottom wall of the guide vane is integrally connected to the rear cover plate.
[0014] Preferably, the top surface of the guide vane is an arc-shaped surface, the thickness of the guide vane gradually decreases from its rear sidewall forward, and the width of the guide vane gradually increases from the front end of the blade backward.
[0015] Preferably, the rear sidewall of the rear cover plate has a concave curved surface.
[0016] This utility model also proposes a fan, including a volute, a drive motor, a flange, and the impeller. The impeller is rotatably disposed inside the volute, the flange is disposed on the back of the volute, the drive motor is connected to the flange, and the output shaft of the drive motor passes through the flange and is rotatably connected to the hub.
[0017] Implementing the embodiments of this utility model will have the following beneficial effects:
[0018] By adopting the aforementioned impeller and setting inclined guide vanes on the blades, an outward resistance is generated on the air drawn into the impeller when the impeller rotates and air is drawn in. At the same time, the air forms a reaction force opposite to this resistance on the guide vanes. The reaction forces of all the guide vanes are superimposed to form a force that can push the impeller inward along its axis, thereby reducing or offsetting the axial force on the motor main shaft, reducing the wear of the ceramic bearing, and extending the service life of the bearing. Attached Figure Description
[0019] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.
[0020] in:
[0021] Figure 1 This is a schematic diagram of the overall structure of the first embodiment of the impeller proposed in this utility model. Figure 1 ;
[0022] Figure 2 This is a schematic diagram of the overall structure of the first embodiment of the impeller proposed in this utility model. Figure 2 ;
[0023] Figure 3 This is a front structural diagram of the first embodiment of the impeller proposed in this utility model;
[0024] Figure 4 for Figure 3 Enlarged diagram of section A in the middle;
[0025] Figure 5 This is a cross-sectional schematic diagram of the guide vanes and blades of the first embodiment of the impeller proposed in this utility model;
[0026] Figure 6 This is a schematic diagram of the overall structure of the second embodiment of the impeller proposed in this utility model;
[0027] Figure 7 This is a cross-sectional schematic diagram of the guide vanes and blades of the second embodiment of the impeller proposed in this utility model;
[0028] Figure 8 This is a schematic diagram of the overall structure of the third embodiment of the impeller proposed in this utility model;
[0029] Figure 9 This is a cross-sectional schematic diagram of the guide vanes and blades of the third embodiment of the impeller proposed in this utility model;
[0030] Figure 10 This is a schematic diagram of the overall structure of the fan proposed in this utility model.
[0031] Reference numerals: 10, hub; 20, rear cover plate; 30, blade; 40, guide vane; 401, front plate; 402, rear plate; 41, guide groove; 50, volute; 60, drive motor; 70, flange. Detailed Implementation
[0032] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains; the terminology used herein in the specification is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention; the terms "comprising" and "having," and any variations thereof, in the specification, claims, and accompanying drawings of this invention are intended to cover non-exclusive inclusion. The terms "first," "second," etc., in the specification, claims, or accompanying drawings of this invention are used to distinguish different objects, not to describe a particular order.
[0033] In this document, the term "embodiment" means that a particular feature, structure, or characteristic described in connection with an embodiment may be included in at least one embodiment of the present invention. The appearance of this phrase in various places throughout the specification does not necessarily refer to the same embodiment, nor is it a separate or alternative embodiment mutually exclusive with other embodiments. It will be explicitly and implicitly understood by those skilled in the art that the embodiments described herein can be combined with other embodiments.
[0034] To enable those skilled in the art to better understand the present invention, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings.
[0035] like Figure 1-10 The image shown is an embodiment provided by this utility model.
[0036] This utility model provides an impeller, mainly used in centrifugal fans, blowers, and other equipment, as shown in the attached drawing. Figure 1-3As shown, the assembly includes a hub 10, a rear cover plate 20, and several blades 30. The hub 10 is coaxially mounted on the rear cover plate 20, and the blades 30 are evenly distributed on the rear cover plate 20 around the axis of the hub 10. The blades 30 are hyperbolic blades 30, also known as twisted blades 30, with a surface that is bi-directionally curved. The front end of the blades 30 is close to the axis of the hub 10, and the rear end of the blades 30 is away from the axis of the hub 10. The outer contour of the rear cover plate 20 is circular, and the rear end of the blades 30 is flush with the circumference of the rear cover plate 20. It is understandable that the front end of blade 30 is the air inlet of the impeller, and the rear end of blade 30 is the air outlet. The outer edge contour of blade 30 is similar to a twisted "S" shape. The rear half of blade 30 is provided with a guide vane 40, which is set along the extension direction of the outer edge of blade 30. If the outer edge contour of blade 30 is divided into two parts according to the "S" shape, then the guide vane 40 is located in the lower half of blade 30, and the extension length of the guide vane 40 does not exceed the lower half of blade 30. The guide vane 40 is oriented towards the rotation of the impeller. The direction is tilted downwards, so that the guide vane 40 and the blade 30 form an inclined angle. When the impeller rotates, the upper surface of the guide vane 40 becomes the windward surface, which generates an outward oblique resistance to the air drawn into the impeller. At the same time, the air drawn into the impeller will also generate an inward oblique reaction force on the upper surface of the guide vane 40. All the reaction forces on the guide vane 40 are superimposed to form a resultant force that can push the impeller inward along its axis, thereby reducing or offsetting the axial force on the motor main shaft. Existing air-suspended and magnetically suspended centrifugal fans require the cooperation of air bearings and thrust bearings during operation. These bearings, with their specially designed airflow channels, are suspended in mid-air. The thrust bearing's force counteracts the axial force generated during operation, stabilizing the fan's normal operation. In contrast, the high-speed centrifugal fan adapted to the impeller in this embodiment is an evolution of air-suspended and magnetically suspended centrifugal fans. Because it uses ceramic bearings suitable for high-speed operation, it cannot use thrust bearings, which are incompatible with ceramic bearings. For ceramic bearing-based high-speed centrifugal fans, the inability to use thrust bearings to counteract axial force is an inherent drawback. In this case, this embodiment compensates for this drawback by incorporating guide vanes 40 on the impeller that generate counter-axial force. During fan operation, the physical state of the ceramic bearing remains unchanged; only the impeller generates axial force during high-speed rotation. However, this axial force is significantly reduced by the reaction force generated by the guide vanes 40, thus slowing down the wear of the ceramic bearing and extending its service life.
[0037] In one specific embodiment, the guide vane 40 is disposed on the outer edge of the blade 30, which is the side of the blade 30 away from the surface of the rear cover plate 20. The height from the rear side of the guide vane 40 to the root of the blade 30 is 1 mm higher than the height from the front side of the guide vane 40 to the root of the blade 30. The front side of the guide vane 40 is the side facing the impeller rotation direction, and the rear side is the opposite. The guide vane 40 as a whole is inclined in a front-low, rear-high manner along the impeller rotation direction. It can be understood that the tilt angle of the guide vane 40 is related to the air resistance it experiences, which in turn affects the counteraxial force generated on the impeller. The greater the resistance experienced by the guide vane 40, the greater the impact on the working efficiency and rotation speed of the impeller.
[0038] Further, refer to the appendix Figure 4 As shown, several guide grooves 41 are distributed on the guide vane 40. The orientation of the guide grooves 41 is the same as the rotation direction of the impeller. The cross-section of the guide grooves 41 is U-shaped or V-shaped, and the depth of the guide grooves 41 is 5mm. The function of the guide grooves 41 is to guide the wind blowing on the upper surface of the guide vane 40, reduce the air disturbance between the blades 30 and the inner wall of the volute 50 when the guide vane 40 rotates with the impeller, and play a role in stabilizing the flow, thereby improving the rotation efficiency of the impeller.
[0039] In one implementation of the above specific embodiments, reference may be made to the appendix. Figure 4-5 As shown, the top wall of the guide vane 40 is set as a flat surface, and the included angle α between the guide vane 40 and the front side wall of the blade 30 is set to 80°-89°. Within this range, the magnitude of the anti-axial force generated by all guide vanes 40 is moderate and closer to the magnitude of the axial force generated by the impeller during operation. This effectively reduces or offsets the force on the bearing, reducing bearing wear, without significantly affecting the impeller's air intake efficiency and rotational speed. Specifically, the two sides of the guide vane 40 extend beyond the two side walls of the blade 30, and the width from the front side of the guide vane 40 to the front side wall of the blade 30 is greater than or equal to the width from the rear side of the guide vane 40 to the rear side wall of the blade 30. This allows for better containment of the air passing between two adjacent blades 30, reducing air dissipation and thus improving air intake efficiency.
[0040] In another embodiment of the above specific embodiments, reference may also be made to the appendix. Figure 6-7As shown, the guide vane 40 is divided into a front plate 401 and a rear plate 402. The widths of the front plate 401 and the rear plate 402 can be set to be the same. The front side of the front plate 401 extends out of the front sidewall of the blade 30 in the direction of impeller rotation. The rear side of the rear plate 402 is flush with the rear sidewall of the blade 30. The included angle β between the front plate 401 and the blade 30 is 80°-89°, and the included angle θ between the rear plate 402 and the blade 30 is 6° smaller than the included angle β between the front plate 401 and the blade 30. Compared to having both sides of the guide vane 40 extend beyond the side walls of the blade 30, extending only the front plate 401 reduces the obstruction area for air intake on the blade 30, thereby increasing the impeller's intake efficiency. Although the increased airflow also increases the axial force, the combined counter-axial force generated by the front plate 401 and rear plate 402 at different tilt angles is also greater, effectively reducing or offsetting the force on the bearing. This reduces bearing wear and improves the impeller's intake efficiency. Furthermore, the connection between the front plate 401 and the front side wall of the blade 30 is machined with rounded corners, which better encloses the air passing between two adjacent blades 30, reducing air loss and thus improving intake efficiency.
[0041] In another specific embodiment, refer to the appendix Figure 8-9 As shown, the rear sidewall of the guide vane 40 is integrally connected to the front sidewall of the blade 30, and the bottom wall of the guide vane 40 is integrally connected to the rear cover plate 20. Compared with suspending the guide vane 40 on the outer edge of the blade 30, the integral connection method is easier to process, and has higher strength and durability. The top surface of the guide vane 40 is arc-shaped, and the thickness of the guide vane 40 is less than the height of the blade 30. The thickness of the guide vane 40 gradually decreases from its rear sidewall forward, while the width of the guide vane 40 gradually increases from the front end of the blade 30 backward. The shape of the guide vane 40 is similar to that of an aircraft wing after inversion. The counter-axial force it generates can also reduce or offset the force on the bearing, thereby reducing bearing wear.
[0042] Further, refer to the appendix Figure 2 As shown, the rear sidewall of the rear cover plate 20 is a concave curved surface, similar to or close to a trumpet shape. This design can reduce the overall weight of the impeller, reduce the energy consumption required for the drive motor 60 to drive the impeller to rotate, and improve the rotation efficiency of the impeller.
[0043] This utility model also proposes a fan, as shown in the attached drawing. Figure 10 As shown, the device includes a volute 50, a drive motor 60, a flange 70, and the aforementioned impeller. The impeller is rotatably disposed inside the volute 50. The flange 70 is disposed on the back of the volute 50. The drive motor 60 is connected to the flange 70. The output shaft of the drive motor 60 passes through the flange 70 and is rotatably connected to the hub 10, thereby driving the impeller.
[0044] Obviously, the embodiments described above are only some embodiments of this utility model, not all embodiments. The accompanying drawings show preferred embodiments of this utility model, but do not limit the patent scope of this utility model. This utility model can be implemented in many different forms; rather, the purpose of providing these embodiments is to provide a more thorough and comprehensive understanding of the disclosure of this utility model. Although this utility model has been described in detail with reference to the foregoing embodiments, those skilled in the art can still modify the technical solutions described in the foregoing specific embodiments, or make equivalent substitutions for some of the technical features. Any equivalent structures made using the content of this utility model specification and drawings, directly or indirectly applied to other related technical fields, are similarly within the patent protection scope of this utility model.
Claims
1. An impeller, characterized in that, include: The wheel hub (10), the rear cover plate (20), and a number of blades (30) are arranged coaxially on the rear cover plate (20), and the number of blades (30) are evenly distributed on the rear cover plate (20) around the axis of the wheel hub (10). The front end of the blade (30) is close to the axis of the hub (10), and the rear end of the blade (30) is away from the axis of the hub (10) and flush with the circumference of the rear cover plate (20). The rear half of the blade (30) is provided with a guide vane (40), which is inclined downward in the direction of rotation of the impeller.
2. The impeller according to claim 1, characterized in that, The guide vane (40) is disposed on the outer edge of the blade (30). The height from the rear side of the guide vane (40) to the root of the blade (30) is 1 mm higher than the height from the front side of the guide vane (40) to the root of the blade (30).
3. The impeller according to claim 2, characterized in that, The guide vane (40) has several guide grooves (41) distributed on it. The depth of the guide grooves (41) is 5 mm, and the orientation of the guide grooves (41) is the same as the rotation direction of the impeller.
4. The impeller according to claim 3, characterized in that, The top wall of the guide vane (40) is a plane, the angle between the guide vane (40) and the blade (30) is 80°-89°, the two sides of the guide vane (40) extend out of the two side walls of the blade (30), and the width from the front side of the guide vane (40) to the front side wall of the blade (30) is greater than or equal to the width from the rear side of the guide vane (40) to the rear side wall of the blade (30).
5. The impeller according to claim 3, characterized in that, The guide vane (40) includes a front plate (401) and a rear plate (402). The front side of the front plate (401) extends out of the front sidewall of the blade (30) in the direction of rotation of the impeller. The rear side of the rear plate (402) is flush with the rear sidewall of the blade (30).
6. The impeller according to claim 5, characterized in that, The angle between the front plate (401) and the blade (30) is 80°-89°, and the angle between the rear plate (402) and the blade (30) is 6° smaller than the angle between the front plate (401) and the blade (30).
7. The impeller according to claim 1, characterized in that, The rear sidewall of the guide vane (40) is integrally connected to the front sidewall of the blade (30), and the bottom wall of the guide vane (40) is integrally connected to the rear cover plate (20).
8. The impeller according to claim 7, characterized in that, The top surface of the guide vane (40) is an arc-shaped surface. The thickness of the guide vane (40) gradually decreases from its rear sidewall to the front, and the width of the guide vane (40) gradually increases from the front end of the blade (30) to the rear.
9. The impeller according to claim 1, characterized in that, The rear sidewall of the rear cover plate (20) is a concave curved surface.
10. A fan, characterized in that, The impeller includes a volute (50), a drive motor (60), a flange (70), and an impeller as described in any one of claims 1-9. The impeller is rotatably disposed within the volute (50), the flange (70) is disposed on the back of the volute (50), the drive motor (60) is connected to the flange (70), and the output shaft of the drive motor (60) passes through the flange (70) and is rotatably connected to the hub (10).