Impeller and crossflow fan

Abstract

This application provides an impeller and a crossflow fan. The crossflow fan includes a volute and an impeller. The volute is fitted over the impeller. The impeller includes a shaft and multiple blades. Each blade is disposed on the outer circumferential surface of the shaft and is spaced apart along the circumferential direction of the shaft. The blades extend from one axial end of the shaft to the other axial end, and the blades and shaft are integrally formed. The volute has a mating section along the circumferential direction of the shaft. The blades rotated to the mating section and together with the mating section form an airflow cavity for conveying airflow. Through the above structural design, this application achieves good structural stability of the impeller, preventing loosening even in high-temperature environments. It also improves the airflow stability of the crossflow fan, increases the airflow frequency, and reduces vibration of the dried material in the application environment.

Description

Technical Field

[0001] This application belongs to the field of crossflow fan technology, and more specifically, relates to an impeller and a crossflow fan. Background Technology

[0002] A crossflow fan is a type of fan where airflow enters radially from one side of the impeller, passes through the interior of the impeller, and exits radially from the other side. The impeller of a crossflow fan typically consists of blades and a support ring. The blades are inserted into the support ring and secured by riveting, which causes the support ring to plastically deform. Riveted blades lack stability and are prone to loosening. Especially in high-temperature environments, the blades and support ring are susceptible to thermal deformation, and the crossflow fan can easily generate metallic dust due to vibration during operation. Summary of the Invention

[0003] The purpose of this application is to provide an impeller and a crossflow fan to solve the technical problem that the blades and support rings of the crossflow fan are prone to loosening in the prior art.

[0004] To achieve the above objectives, the technical solution adopted in this application is as follows: An impeller is provided for use in a crossflow fan. The crossflow fan includes a volute, and the impeller is disposed within the volute. The impeller includes a shaft and multiple blades, each blade being disposed on the outer circumferential surface of the shaft. The blades are spaced apart along the circumferential direction of the shaft, extending from one axial end of the shaft to the other axial end. The blades and the shaft are integrally formed. The volute has a mating section along the circumferential direction of the shaft. The blades rotated to the mating section and together with the mating section form an airflow cavity for conveying airflow.

[0005] In some embodiments, the shaft and each of the blades are integrally formed by stretching an alloy material to a predetermined length.

[0006] In some embodiments, the shaft core is cylindrical; Alternatively, the shaft core may be a solid structure.

[0007] In some embodiments, the impeller further includes a collar and a rotating shaft, the shaft core is cylindrical, the collar is inserted into the end of the shaft core and fixedly connected to the shaft core, and the rotating shaft is fixedly connected to the collar; Alternatively, the impeller may further include a rotating shaft, which is fixedly connected to the shaft core.

[0008] On the other hand, this application also provides a crossflow fan, including a volute and the aforementioned impeller. The impeller includes a shaft and a plurality of blades. The volute is sleeved outside the impeller. The volute has a mating section along the circumference of the shaft. The blades rotated to the mating section and together with the mating section form an airflow cavity for conveying airflow.

[0009] In some embodiments, the volute has an air inlet and an air outlet, the mating section is disposed near the air inlet and is located downstream of the air inlet along the rotation direction of the shaft, external airflow enters the airflow chamber through the air inlet, and the airflow in the airflow chamber flows to the air outlet under the action of centrifugal force generated when the shaft rotates.

[0010] In some embodiments, the mating section is arc-shaped, the mating section and the shaft are coaxially arranged, and the inner side of the mating section and the top of the corresponding blade have a first gap.

[0011] In some embodiments, the first gap ranges from 1 mm to 3 mm.

[0012] In some embodiments, the central angle of the mating segment ranges from 45 degrees to 75 degrees.

[0013] In some embodiments, the crossflow fan has a first side and a second side disposed opposite to each other along a first direction, the air inlet is formed on the first side, the air outlet is formed on the second side, and the first direction is perpendicular to the axial direction of the shaft core.

[0014] The beneficial effects of the impeller and crossflow fan provided in this application are as follows: By setting a shaft core and integrally forming each blade on the outer circumference of the shaft core, the connection stability between the blades and the shaft core is good, and there is no risk of loosening even in high-temperature environments. At the same time, the root of the blade is fixed on the shaft core and extends from the inside to the outside, eliminating the need for secondary processing to expose the blades, resulting in higher impeller production efficiency, more precise blade shape and position, and better influence on wind speed consistency. In addition, since the blades are fixed outside the shaft core, and the blades rotating to the mating section together with the mating section form an airflow cavity for conveying airflow, that is, when the impeller rotates, the blades can drive the airflow circumferentially, and the airflow is conveyed through the airflow cavity. The airflow is conveyed along the outer circumference of the shaft core. Compared with the prior art where the airflow needs to be conveyed across the impeller, the embodiment of this application changes the airflow field, so that the airflow movement is not affected by centrifugal eddies, thereby improving the outlet airflow stability of the crossflow fan, increasing the wind frequency, and reducing the shaking of the dried object in the application scenario. Attached Figure Description

[0015] To more clearly illustrate the technical solutions in the embodiments of this application, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0016] Figure 1This is a side view of the crossflow fan provided in an embodiment of this application.

[0017] Figure 2 This is a cross-sectional view of the crossflow fan provided in an embodiment of this application, perpendicular to the axial direction.

[0018] Figure 3 This is a three-dimensional structural diagram of the impeller body in an embodiment of this application.

[0019] Figure 4 This is a schematic cross-sectional view of the impeller body perpendicular to the axial direction, provided in an embodiment of this application.

[0020] Figure 5 This is a three-dimensional structural diagram of the impeller provided in an embodiment of this application.

[0021] Figure 6 This is a schematic cross-sectional view of the impeller parallel to the axial direction provided in an embodiment of this application.

[0022] The following are the labeling elements in the figure: 100 Impeller; 110 Impeller body; 111 Shaft core; 112 Blade; 120 Shaft collar; 130 Rotating shaft; 200 Volute; 210 First housing; 220 Second housing; 221 First air guide section; 222 Fitting section; 223 Guide section; 224 Second air guide section; 230 Air inlet; 240 Air outlet; 300 Mounting base; 400 Airflow cavity; 500 First side; 600 Second side; H1 First thickness; H2 Second thickness; X First direction; Y Second direction; Z Axial direction. Detailed Implementation

[0023] To make the technical problems, technical solutions, and beneficial effects to be solved by this application clearer, the following detailed description is provided in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and are not intended to limit the scope of this application.

[0024] It should be noted that when a component is referred to as being "fixed to" or "set on" another component, it can be directly on or indirectly on that other component. When a component is referred to as being "connected to" another component, it can be directly connected to or indirectly connected to that other component.

[0025] It should be understood that the terms "length", "width", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this application 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 application.

[0026] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this application, "multiple" means two or more, unless otherwise explicitly specified.

[0027] As described in the background section, the impeller of a crossflow fan generally includes blades and a support ring. After the blades are inserted into the support ring, they are fixed by riveting, which causes the support ring to undergo plastic deformation. However, riveted blades lack stability and are prone to loosening. Especially when used in high-temperature environments, the blades and support ring are prone to thermal deformation, and the fan is prone to generating metallic dust due to vibration during operation.

[0028] Furthermore, the working principle of a traditional crossflow fan is as follows: a motor drives an impeller to rotate, causing air to enter the impeller through the inlet. Under the action of an eccentric vortex, the air passes through the impeller blades twice and is finally evenly delivered laterally from the outlet. The problem with this principle is that the eccentric vortex is unstable, resulting in a low air frequency and discontinuous airflow. This can cause the dried material to vibrate continuously in certain scenarios, affecting production quality.

[0029] It should be noted that the horizontal direction of a crossflow fan is the same as the axial direction of the impeller, which will be referred to as the axial direction from now on.

[0030] To address the aforementioned technical problems, this application provides an impeller 100 and a crossflow fan.

[0031] Please refer to the following: Figures 1 to 4 The impeller 100 provided in the embodiments of this application will now be described.

[0032] The impeller 100 is used in a crossflow fan, which includes a volute 200 having an air inlet 230 and an air outlet 240.

[0033] The impeller 100 is disposed in the volute 200. The impeller 100 includes a shaft core 111 and a plurality of blades 112. Each blade 112 is disposed on the outer circumferential surface of the shaft core 111. The blades 112 are spaced apart along the circumferential direction of the shaft core 111. The blades 112 extend from one axial Z end of the shaft core 111 to the other axial Z end of the shaft core 111. The blades 112 and the shaft core 111 are integrally formed. The volute 200 has a mating section 222 along the circumferential direction of the shaft core 111. The blades 112 rotated to the mating section 222 and together with the mating section 222 form an airflow cavity 400 for conveying airflow.

[0034] The shaft core 111 is a rotating structure. The shaft core 111 is connected to the electric drive component of the crossflow fan through the rotating shaft 130. The electric drive component drives the shaft core 111 to rotate through the rotating shaft 130, thereby driving the entire impeller 100 to rotate in the volute 200.

[0035] Each blade 112 is evenly spaced around the shaft core 111. Each blade 112 extends linearly from one end of the shaft core 111 along the axial direction Z to the other end. The cross-section of each blade 112 perpendicular to the axial direction Z is arc-shaped or approximately arc-shaped. Each blade 112 has a root and a tip. The root of the blade 112 is integrally connected to the shaft core 111, and the tip of the blade 112 is positioned away from the shaft core 111. Each blade 112 extends from its root along a first rotation direction M1 and along an arc to its tip. The first rotation direction M1 is a circumferential direction with the centerline of the shaft core 111 as the center of rotation. When the shaft core 111 rotates along the first rotation direction M1, the blades 112 can drive the airflow along the first rotation direction M1.

[0036] The blade 112 rotates to the mating section 222 and together with the mating section 222 form an airflow cavity 400 for conveying airflow. Here, the mating section 222 refers to the part of the volute 200 that is closest to the blade 112 and has a shape close to an arc. This allows the adjacent blade 112 and the volute 200 to form the airflow cavity 400 when the blade 112 rotates to the position corresponding to the mating section 222. During the rotation of the shaft core 111 along the first rotation direction M1, the external airflow enters the volute 200 from the air inlet 230 and enters the space between the adjacent blades 112 that have rotated to the air inlet 230. As the shaft core 111 rotates, the airflow between the adjacent blades 112 is also carried to the mating section 222 of the volute 200. The mating section 222 blocks the airflow between the adjacent blades 112 to form a stable airflow, that is, the airflow is stably delivered through the airflow cavity 400. Finally, under the rotation of the shaft core 111, the airflow in the airflow cavity 400 is thrown tangentially towards the air outlet 240 under the action of centrifugal force, forming a stable wind field at a certain rotation speed.

[0037] The impeller 100 provided in this embodiment features a shaft core 111, with each blade 112 integrally formed on the outer circumferential surface of the shaft core 111. This design ensures good connection stability between the blades 112 and the shaft core 111, preventing loosening even in high-temperature environments. Furthermore, the roots of the blades 112 are fixed to the shaft core 111, extending outwards without requiring secondary processing to expose the blades 112. This results in higher production efficiency for the impeller 100, more precise shape and position of the blades 112, and better consistency in wind speed. Furthermore, since the blades 112 are fixed outside the shaft core 111, and the blades 112 rotated to the mating section 222 together with the mating section 222 form an airflow cavity 400 for conveying airflow, when the impeller 100 rotates, the blades 112 can drive the airflow in the circumferential direction and convey the airflow through the airflow cavity 400. The airflow is conveyed along the outer periphery of the shaft core 111. Compared with the prior art where the airflow needs to be conveyed across the impeller 100, the embodiment of this application changes the airflow field, so that the airflow movement is not affected by centrifugal eddies, thereby improving the airflow stability of the crossflow fan, increasing the airflow frequency, and reducing the shaking of the dried object in the usage scenario.

[0038] In some embodiments, please refer to Figure 3 and Figure 4 The shaft core 111 and each blade 112 are formed by stretching an alloy material to a predetermined length. Specifically, the impeller 100 includes an impeller body 110, which includes a shaft core 111 and blades 112. The impeller body 110 is formed by stretching an alloy material to a predetermined length. The stretching process has advantages such as high dimensional accuracy, good surface finish, good mechanical properties, material saving, and high forming efficiency. It is understood that in other embodiments of this application, the shaft core 111 and blades 112 can also be integrally formed by machining; or, in other embodiments, the shaft core 111 and blades 112 can also be integrally injection molded, without limitation here.

[0039] Optionally, the two end faces of the blade 112 along the axial direction Z are flush with the two end faces of the shaft core 111 along the axial direction Z.

[0040] In some embodiments, please refer to Figures 2 to 4 The shaft core 111 is cylindrical, that is, the shaft core 111 is hollow. This can reduce the weight of the shaft core 111, reduce the load when the impeller 100 rotates, reduce the rotational power consumption of the impeller 100, and also reduce the stretching difficulty of the shaft core 111 and the blade 112.

[0041] Optionally, please refer to Figure 4The shaft core 111 has a first thickness H1 in the radial direction, and the blade 112 has a second thickness H2 in the first rotation direction M1. The first thickness H1 and the second thickness H2 are approximately equal, for example, the first thickness H1 is equal to the second thickness H2, or the first thickness H1 is slightly less than the second thickness H2, or the first thickness H1 is slightly greater than the second thickness H2, wherein the difference between the first thickness H1 and the second thickness H2 is less than one-quarter of the first thickness H1. This design makes the first thickness H1 of the shaft core 111 sufficiently small, reducing the difficulty of stretching the shaft core 111 and the blade 112 together, and also making the weight of the shaft core 111 relatively small, which is beneficial for the rotational drive of the impeller 100.

[0042] In other embodiments of this application, the shaft core 111 may also be a solid structure, that is, the shaft core 111 is cylindrical, which is not the only limitation here.

[0043] In some embodiments, please refer to Figure 5 and Figure 6 The impeller 100 also includes a collar 120 and a rotating shaft 130. The shaft core 111 is cylindrical, and the collar 120 is inserted into and fixedly connected to the end of the shaft core 111. The rotating shaft 130 is fixedly connected to the collar 120. The collar 120 connects the rotating shaft 130 and the shaft core 111, allowing the impeller 100 to be connected to a rotary drive component via the rotating shaft 130, thus enabling the rotary drive component to rotate the impeller 100.

[0044] In some embodiments, the shaft 130 and the collar 120 are integrally formed, meaning they can be integrally molded. During assembly, the collar 120 is directly inserted into the end of the shaft core 111, and the collar 120 and the shaft core 111 are welded together, reducing the connection difficulty between the shaft 130 and the collar 120. Understandably, in other embodiments of this application, the shaft 130 and the collar 120 can also be separately configured and integrally connected. For example, the shaft 130 and the collar 120 can be connected as one piece by welding or screw locking. Furthermore, in other embodiments, when the shaft core 111 is a solid structure, the collar 120 can be disposed on the outer side of the end of the shaft core 111, and the collar 120 and the shaft core 111 can be fixed, specifically by welding or screw locking.

[0045] In some other embodiments of this application, the impeller 100 further includes a rotating shaft 130, which is fixedly connected to a shaft core 111. That is, in this embodiment, the shaft collar 120 is not required, and the rotating shaft 130 and the shaft core 111 are directly connected. As an example, the shaft core 111 is cylindrical, and one end of the rotating shaft 130 is inserted into the shaft core 111 and is connected to the shaft core 111 by welding, interference fit, or screws. As another example, the shaft core 111 is a solid structure, and the rotating shaft 130 is attached to the outer end of the shaft core 111, and the rotating shaft 130 and the shaft core 111 are connected by welding or screws.

[0046] On the other hand, please see Figures 1 to 4 This application also provides a crossflow fan, including a volute 200 and the aforementioned impeller 100. The impeller 100 includes a shaft core 111 and multiple blades 112. The volute 200 is sleeved on the outside of the impeller 100. The volute 200 has a mating section 222 along the circumference of the shaft core 111. The blades 112 rotated to the mating section 222 and together with the mating section 222 form an airflow cavity 400 for conveying airflow. The crossflow fan provided in this application embodiment, through the aforementioned impeller 100 configuration, makes the crossflow fan structurally stable and can operate normally even in high-temperature environments. Furthermore, through the structural design of the shaft core 111, blades 112, and volute 200, the airflow field is changed, so that the airflow movement is not affected by centrifugal vortices, thereby improving the outlet airflow stability of the crossflow fan, increasing the airflow frequency, and reducing the shaking of the dried object in the usage scenario.

[0047] In some embodiments, please refer to Figure 2 The volute 200 has an air inlet 230 and an air outlet 240. The mating section 222 is located near the air inlet 230 and is located downstream of the air inlet 230 along the rotation direction of the shaft core 111. External airflow enters the airflow chamber 400 through the air inlet 230. Under the action of centrifugal force generated when the shaft core 111 rotates, the airflow in the airflow chamber 400 flows to the air outlet 240.

[0048] The mating section 222 is the part of the volute 200 that mates with the top of the blade 112 along the circumference of the shaft core 111. The mating section 222 is located downstream of the air inlet 230 along the rotation direction of the shaft core 111 (i.e., the first rotation direction M1). That is, when the shaft core 111 rotates with the blades 112, each blade 112 first passes through the air inlet 230, then through the mating section 222, and finally through the air outlet 240. External airflow first enters between the blades 112 from the air inlet 230. The blades 112 carry the airflow into the airflow cavity 400 formed by the blades 112 and the mating section 222, and then, under the centrifugal force of the rotating shaft core 111, it is thrown towards the air outlet 240.

[0049] In some embodiments, please refer to Figure 2 The mating section 222 is arc-shaped and is coaxial with the shaft core 111. The inner side of the mating section 222 and the top of the corresponding blade 112 have a first gap.

[0050] Since the blade 112 is arc-shaped and the top of the blade 112 facing the mating section 222 is not a plane, the first gap refers to the distance between the inner side of the mating section 222 and the point or line in the corresponding blade 112 that is closest to the mating section 222.

[0051] In this embodiment, by setting the mating section 222 to an arc shape, the mating section 222 is adapted to the distribution trajectory of the top of each blade 112, so that the first gap between the mating section 222 and the blade 112 can be as small as possible, so that the shape of the airflow cavity 400 formed by the mating section 222 and the two adjacent blades 112 is stable, and can drive the airflow to flow stably under the action of centrifugal force to form a stable wind field.

[0052] In some embodiments, the first gap ranges from 1mm to 3mm, for example, the first gap can be 1mm, 1.2mm, 1.4mm, 1.6mm, 1.8mm, 2.0mm, 2.2mm, 2.4mm, 2.6mm, 2.8mm, or 3.0mm. The first gap is a key factor in forming a stable airflow between the blade 112 and the mating section 222. If the first gap is too small, friction between the blade 112 and the mating section 222 will occur, affecting the rotation of the impeller 100 and causing instability in the airflow cavity 400. Conversely, if the first gap is too large, excessive airflow that cannot be driven by the blade 112 will accumulate in the first gap during the rotation of the shaft core 111, resulting in uneven airflow velocity and an unstable airflow. This application limits the size of the first gap to ensure smooth rotation of the impeller 100 and a stable airflow between the blade 112 and the volute 200, thereby stabilizing the outlet airflow of the crossflow fan and ensuring uniform outlet airflow velocity.

[0053] In some embodiments, please refer to Figure 2 The central angle range of section 222 is 45 degrees to 75 degrees.

[0054] Among them, the mating section 222 is arc-shaped, and the central angle of the mating section 222 is the angle between the arc length of the mating section 222 and the center of the mating section 222. When the mating section 222 and the shaft core 111 are coaxial, the central angle of the mating section 222 is the included angle between the connecting lines of the two opposite sides of the mating section 222 along the circumferential direction to the center of the shaft core 111.

[0055] The central angle of the mate segment 222 can be 45 degrees, 50 degrees, 55 degrees, 60 degrees, 65 degrees, 70 degrees or 75 degrees, etc. The central angle of the mating section 222 indicates the arc length of the mating section 222. The arc length of the mating section 222 represents how many blades 112 can surround the mating section 222 to form an airflow cavity 400, which means that when the impeller 100 rotates, it can drive the airflow to run stably. Therefore, the central angle of the mating section 222 cannot be too small. If it is too small, only a small part of the wind field will be stable during the rotation of the impeller 100, while the wind field in other places will be unstable, which will result in the wind field of the entire impeller 100 being unstable. The central angle of the mating section 222 cannot be too large either. If it is too large, the mating section 222 will block the airflow. When the blades 112 drive the airflow out, the airflow flows from the tangential direction of the blades 112 to the air outlet 240. Therefore, there needs to be a guide section 223 between the blades 112 and the air outlet 240 to avoid the blades 112, and the distance between the guide section 223 and the blades 112 is relatively large.

[0056] Optionally, the central angle of the mating segment 222 is 60 degrees.

[0057] In some embodiments, please refer to Figure 2 The volute 200 includes a first housing 210 and a second housing 220. The first end of the first housing 210 and the third end of the second housing 220 are spaced apart to form an air inlet 230. The second end of the first housing 210 and the fourth end of the second housing 220 are spaced apart to form an air outlet 240. The second housing 220 is located downstream of the air inlet 230 along the rotation direction of the shaft core 111. The mating section 222 is located near the third end of the second housing 220.

[0058] In some embodiments, please refer to Figure 2 The impeller 100 has a first side 500 and a second side 600 arranged opposite to each other along the first direction X. An air inlet 230 is located on the first side 500, and an air outlet 240 is located on the second side 600. A first housing 210 and a second housing 220 are spaced apart along the second direction Y. The first direction X, the second direction Y, and the axial direction Z are all perpendicular to each other. In this embodiment, by placing the air inlet 230 and the air outlet 240 on the first side 500 and the second side 600 respectively, the external airflow is drawn in from the first side 500 of the crossflow fan and discharged from the second side 600. This improves the uniformity of the airflow velocity at the air outlet 240 along the axial direction Z, enhances the drying quality of the dried material, and improves the production yield and safety of the battery.

[0059] For details, please refer to Figure 2The first end of the first housing 210 and the third end of the second housing 220 both extend to the first side 500 and are spaced apart on the first side 500 to form an air inlet 230. The second end of the first housing 210 and the fourth end of the second housing 220 both extend to the second side 600 and are spaced apart on the second side 600 to form an air outlet 240.

[0060] For details, please refer to Figure 2 The second housing 220 includes a first air guide section 221, a mating section 222, a flow guide section 223, and a second air guide section 224. The first air guide section 221, the mating section 222, and the flow guide section 223 are connected sequentially via the second air guide section 224. A third end is located at the end of the first air guide section 221 opposite to the mating section 222, and a fourth end is located at the end of the second air guide section 224 opposite to the flow guide section 223. The first air guide section 221 is arranged approximately perpendicular to the second direction Y, and the corresponding portions of the first air guide section 221 and the first housing 210 are spaced apart to form an air inlet 230. The normal direction of the second air guide section 224 is perpendicular to the second direction Y, and the corresponding portions of the second air guide section 224 and the first housing 210 are spaced apart to form an air outlet 240. The cross section of the mating section 222 perpendicular to the axial direction Z is arc-shaped. The guide section 223 connects the mating section 222 and the second guide section 224. The distance between the guide section 223 and the blade 112 gradually increases from the mating section 222 to the second guide section 224, so as to guide the airflow in the airflow cavity 400 to flow tangentially to the air outlet 240.

[0061] In some embodiments, the crossflow fan further includes two mounting bases 300 and an electric drive unit. The two mounting bases 300 are spaced apart along the Z-axis. An impeller 100 is disposed between the two mounting bases 300, and the opposite ends of the impeller 100 are rotatably mounted on the two mounting bases 300 via a rotating shaft 130. A volute 200 is connected between the two mounting bases 300 and is sleeved on the outside of the impeller 100. The electric drive unit is mounted on one of the mounting bases 300 and is used to output rotational motion. The output end of the electric drive unit is connected to the rotating shaft 130, and the electric drive unit is used to drive the impeller 100 to rotate via the rotating shaft 130. The rotation of the impeller 100 drives the external airflow to enter the crossflow fan from the air inlet 230, and under the drive of the blades 112 of the impeller 100, it flows around the outer periphery of the shaft core 111 to the air outlet 240, and then flows from the air outlet 240 to the crossflow fan.

[0062] The above description is merely a preferred embodiment of this application and is not intended to limit this application. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. An impeller used in a crossflow fan, the crossflow fan comprising a volute, characterized in that, The impeller is disposed in the volute and includes a shaft core and a plurality of blades. Each blade is disposed on the outer circumferential surface of the shaft core and is spaced apart along the circumferential direction of the shaft core. The blades extend from one axial end of the shaft core to the other axial end of the shaft core and the blades and the shaft core are integrally formed. The volute has a mating section along the circumferential direction of the shaft core. The blades rotated to the mating section and the mating section together form an airflow cavity for conveying airflow.

2. The impeller as described in claim 1, characterized in that, The shaft and each blade are integrally formed by stretching an alloy material to a preset length.

3. The impeller as described in claim 1 or 2, characterized in that, The shaft core is cylindrical; Alternatively, the shaft core may be a solid structure.

4. The impeller as described in claim 1 or 2, characterized in that, The impeller also includes a collar and a rotating shaft. The shaft core is cylindrical. The collar is inserted into the end of the shaft core and fixedly connected to the shaft core. The rotating shaft is fixedly connected to the collar. Alternatively, the impeller may further include a rotating shaft, which is fixedly connected to the shaft core.

5. A crossflow fan, characterized in that, The impeller includes a volute and an impeller as described in any one of claims 1 to 4. The impeller includes a shaft and a plurality of blades. The volute is sleeved on the outside of the impeller. The volute has a mating section along the circumference of the shaft. The blades rotated to the mating section and the mating section together form an airflow cavity for conveying airflow.

6. The crossflow fan as described in claim 5, characterized in that, The volute has an air inlet and an air outlet. The mating section is located near the air inlet and downstream of the air inlet along the rotation direction of the shaft. External airflow enters the airflow chamber through the air inlet. Under the centrifugal force generated when the shaft rotates, the airflow in the airflow chamber flows towards the air outlet.

7. The crossflow fan as described in claim 5, characterized in that, The mating section is arc-shaped and coaxially arranged with the shaft core. The inner side of the mating section and the top of the corresponding blade have a first gap.

8. The crossflow fan as described in claim 7, characterized in that, The first gap ranges from 1mm to 3mm.

9. The crossflow fan as described in claim 7, characterized in that, The central angle of the mating section ranges from 45 degrees to 75 degrees.

10. The crossflow fan as described in claim 6, characterized in that, The crossflow fan has a first side and a second side arranged opposite to each other along a first direction, the air inlet is formed on the first side, the air outlet is formed on the second side, and the first direction is perpendicular to the axial direction of the shaft core.

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