Fan, and air handling apparatus

Abstract

Disclosed in the present application are a fan and an air handling apparatus. The fan comprises a stator assembly (100), a rotating shaft (200), a rotor assembly (300) and a fan wheel (400). The stator assembly (100) comprises a stator body, in which an accommodating cavity (111) is provided; a bearing seat (120), in which a bearing chamber (121) is provided; and a bearing (130), wherein the bearing seat (120) is mounted in the accommodating cavity (111), and the bearing (130) is fixedly mounted in the bearing chamber (121). The rotating shaft (200) is arranged passing through the bearing chamber (121) and is mounted on the bearing (130); the rotor assembly (300) is mounted on the rotating shaft (200) and is arranged around the outer periphery of the stator assembly (100); and the fan wheel (400) is located on one axial side of the rotor assembly (300) and is mounted on the rotating shaft (200).

Description

Fans and air handling equipment

[0001] Cross-reference to related applications

[0002] This application claims priority to Chinese patent applications filed on October 29, 2024, with application number 202411525156.1 entitled "Fan and Air Handling Equipment" and application number 202422626052.1 entitled "Fan and Air Handling Equipment", the entire contents of which are incorporated herein by reference. Technical Field

[0003] This application relates to the field of fan technology, and in particular to a fan and air handling equipment. Background Technology

[0004] In the motor assembly of a wind turbine, the rotor and shaft are typically supported radially by a sliding bearing assembly. However, in related technologies, the structural rigidity of the sliding bearing assembly is poor. During wind turbine operation, this can cause the rotation axis of the rotor and shaft to deviate from the central axis of the stator, resulting in poor rotational accuracy. Especially in high temperature and high humidity environments, this can easily cause the motor assembly to experience rotor rubbing failure. Summary of the Invention

[0005] This application aims to solve at least one of the technical problems existing in the prior art. To this end, this application proposes a fan with a bearing housing structure of high rigidity, which can provide stable radial support for the impeller, rotor assembly and shaft, effectively ensuring rotational accuracy and reducing the risk of rotor rubbing failure.

[0006] This application also provides an air handling device having the above-described fan.

[0007] A wind turbine according to a first aspect embodiment of this application includes a stator assembly comprising a stator body, a bearing housing, and a bearing. The stator body has a receiving cavity, the bearing housing is installed in the receiving cavity, the bearing housing has a bearing chamber, and the bearing is fixedly installed in the bearing chamber. A rotating shaft passes through the bearing chamber and is installed on the bearing. A rotor assembly is installed on the rotating shaft and arranged around the outer periphery of the stator assembly. A wind turbine is located on one side of the rotor assembly along the axial direction and is installed on the rotating shaft. The bearing housing is an elastic structural component with a radial stiffness of k. The total mass of the rotating shaft, the rotor assembly, and the wind turbine is m. The imbalance of the rotating shaft, the rotor assembly, and the wind turbine is U. The maximum angular velocity of the rotor assembly is ω, satisfying: g is the acceleration due to gravity.

[0008] The fan according to the first aspect embodiment of this application has at least the following beneficial effects: by installing a bearing housing between the stator body and the bearing, the bearing housing being an elastic structural component, and the radial stiffness k of the bearing housing satisfying... This means selecting a bearing housing with greater radial stiffness based on the total weight and imbalance of the shaft, rotor assembly, and impeller. This increases the structural stiffness of the bearing housing, enabling it to withstand the radial forces applied by the shaft, rotor assembly, and impeller, and providing stable radial support. This effectively ensures the rotational accuracy of the shaft, rotor assembly, and impeller, and guarantees stable support even in high-temperature and high-humidity environments. Consequently, it reduces the risk of rotor rubbing failure, effectively improves the operational stability of the fan, and reduces vibration and noise.

[0009] According to some embodiments of this application, the stator body and the bearing housing are interference fit.

[0010] According to some embodiments of this application, the stator body includes a first snap-fit ​​portion, and the bearing housing includes a second snap-fit ​​portion, the second snap-fit ​​portion engaging with the first snap-fit ​​portion to restrict the bearing housing's axial degree of freedom.

[0011] According to some embodiments of this application, the first snap-fit ​​portion is a protrusion protruding from the inner peripheral wall of the receiving cavity, and the second snap-fit ​​portion is a recessed portion recessed relative to the outer peripheral wall of the bearing seat, wherein the protrusion is received in the recess.

[0012] According to some embodiments of this application, one end of the bearing housing is provided with a guide portion, which is used to guide the protrusion into the recess.

[0013] According to some embodiments of this application, the bearing housing includes an arcuate inner wall that is recessed toward the outer peripheral wall of the bearing seat along the radial direction of the rotating shaft, and the bearing includes an arcuate outer wall that protrudes toward the arcuate inner wall along the radial direction of the rotating shaft, and the arcuate outer wall abuts against the arcuate inner wall.

[0014] According to some embodiments of this application, the bearing housing includes a first end face perpendicular to the axial direction, the first end face facing the wind turbine, and the bearing includes a second end face located at one end along the axial direction, the second end face abutting against the first end face.

[0015] According to some embodiments of this application, the rotor assembly includes a second molding body and a plurality of magnets. The second molding body includes a first end plate and an annular plate connected to one side of the first end plate along the axial direction. The plurality of magnets are mounted on the annular plate and arranged at circumferential intervals along the stator assembly. The impeller is connected to the other side of the first end plate along the axial direction.

[0016] According to some embodiments of this application, the rotor assembly includes a second encapsulated body and a magnetic ring. The second encapsulated body includes a second end plate. The magnetic ring is mounted on one side of the second end plate along the axial direction and arranged around the outer periphery of the stator assembly. The impeller is connected to the other side of the second end plate along the axial direction.

[0017] According to some embodiments of this application, the second molding body and the wind turbine are integrally molded parts.

[0018] An air handling apparatus according to a second aspect of this application includes a fan according to a first aspect of this application.

[0019] The air handling apparatus according to the second aspect embodiment of this application has at least the following beneficial effects: Because the air handling apparatus uses the aforementioned fan, and a bearing housing is installed between the stator body and the bearing, the bearing housing is an elastic structural component, and the radial stiffness k of the bearing housing satisfies… This means selecting a bearing housing with greater radial stiffness based on the total weight and imbalance of the shaft, rotor assembly, and impeller. This increases the structural stiffness of the bearing housing, enabling it to withstand the radial forces applied by the shaft, rotor assembly, and impeller, and providing stable radial support. This effectively ensures the rotational accuracy of the shaft, rotor assembly, and impeller, and guarantees stable support even in high-temperature and high-humidity environments. Consequently, it reduces the risk of rotor rubbing failure, effectively improves the operational stability of the fan, and reduces vibration and noise.

[0020] Additional aspects and advantages of this application will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of this application. Attached Figure Description

[0021] The present application will be further described below with reference to the accompanying drawings and embodiments, wherein:

[0022] Figure 1 is a cross-sectional view of the fan in an embodiment of this application;

[0023] Figure 2 is a cross-sectional view of the connection between the first molding compound and the stator core in an embodiment of this application;

[0024] Figure 3 is a cross-sectional view of the bearing housing in an embodiment of this application;

[0025] Figure 4 is a cross-sectional view of the bearing in an embodiment of this application;

[0026] Figure 5 is a cross-sectional view of the connection between the rotor assembly and the shaft in another embodiment of this application;

[0027] Figure 6 is a cross-sectional view of the connection between the rotor assembly and the shaft in another embodiment of this application.

[0028] Reference numerals: Stator assembly 100; First encapsulated body 110; Receiving cavity 111; First snap-fit ​​part 112; Bearing seat 120; Bearing chamber 121; Arc-shaped inner wall 1211; First end face 1212; Second snap-fit ​​part 122; Guide part 123; Bearing 130; Arc-shaped outer wall 131; Second end face 132; Oil groove 133; Dust cover 134; Stator core 140; End cover 150; Shaft 200; Rotor assembly 300; Second encapsulated body 310; First end plate 311; Annular plate 312; Second end plate 313; Magnet 320; Magnetic ring 330; Magnetic guide ring 340; Wind turbine 400. Detailed Implementation

[0029] The embodiments of this application are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this application, and should not be construed as limiting this application.

[0030] In the description of this application, it should be understood that the orientation descriptions, such as up, down, front, back, left, right, 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.

[0031] In the description of this application, "several" means one or more, "more than" means two or more, "greater than," "less than," and "exceeding" are understood to exclude the stated number, while "above," "below," and "within" are understood to include the stated number. The use of "first" and "second" in the description is merely for distinguishing technical features and should not be construed as indicating or implying relative importance, or implicitly indicating the number of indicated technical features, or implicitly indicating the order of the indicated technical features.

[0032] In the description of this application, unless otherwise expressly defined, terms such as setting, installing, connecting, assembling, and cooperating should be interpreted broadly, and those skilled in the art can reasonably determine the specific meaning of the above terms in this application in conjunction with the specific content of the technical solution.

[0033] Referring to Figures 1 to 6, a first aspect of this application provides a fan used in an air handling device. This air handling device can be an air conditioner, a evaporative cooler, an air purifier, a humidifier, etc. For example, the fan serves as part of the air outlet device of the indoor unit of an air conditioner, used to blow cool or warm air from the air conditioner into the room.

[0034] Referring to Figures 1 and 2, it can be understood that the fan includes a motor assembly, a shaft 200, and a rotor 400. The motor assembly is an external rotor motor and includes a stator assembly 100 and a rotor assembly 300. Specifically, the stator assembly 100 includes a stator core 140, a first plastic sealant 110, a bearing housing 120, a bearing 130, and an end cap 150. The first plastic sealant 110 is a plastic structure covering the stator core 140, forming a single unit with the stator core 140. The entirety of the first plastic sealant 110 and the stator core 140 constitutes the stator body. The first plastic sealant 110 may completely cover the outer periphery of the stator core 140, or the outer periphery of the stator core 140 may be exposed outside the first plastic sealant 110. The end cap 150 is installed at one axial end of the first molding compound 110. For example, the end cap 150 is glued, snapped, or connected to the first molding compound 110 by fasteners such as screws. The axial direction is the direction of the central axis of the stator assembly 100. The direction around the central axis of the stator assembly 100 is the circumferential direction. The direction perpendicular to the central axis of the stator assembly 100 and pointing from the central axis of the stator assembly 100 to the outer periphery of the stator assembly 100, and the opposite direction, is the radial direction.

[0035] Referring to Figure 2, it can be understood that a receiving cavity 111 is provided in the middle of the first molding compound 110. The cross-section of the receiving cavity 111 (perpendicular to the axial direction) is circular, and the central axis of the receiving cavity 111 coincides with the central axis of the stator assembly 100. The two ends of the receiving cavity 111 along the central axis direction respectively penetrate the end walls of the two ends of the first molding compound 110 along the axial direction.

[0036] Referring to Figures 1 and 3, it can be understood that the bearing housing 120 is installed in the receiving cavity 111 and fixed to the first plastic seal 110. A bearing chamber 121 is provided in the middle of the bearing housing 120. The cross-section of the bearing chamber 121 is also circular, and the central axis of the bearing chamber 121 coincides with the central axis of the receiving cavity 111. Both ends of the bearing chamber 121 along the central axis penetrate the end walls of both ends of the bearing housing 120 along the axial direction. In other words, the bearing housing 120 is approximately a sleeve structure.

[0037] Referring to Figure 1, it can be understood that the bearing housing 120 and the first molding compound 110 are interference-fitted, thereby fixing the bearing housing 120 to the first molding compound 110 and preventing the bearing housing 120 from rotating relative to the first molding compound 110. Alternatively, the bearing housing 120 and the first molding compound 110 can be connected by a structure of mutually constraining ribs and grooves in the circumferential direction to prevent the bearing housing 120 from rotating relative to the first molding compound 110; or the bearing housing 120 and the first molding compound 110 can be fitted by a key connection; or the outer peripheral wall of the bearing housing 120 and the inner peripheral wall of the receiving cavity 111 can be bonded together to fix the bearing housing 120 to the first molding compound 110.

[0038] Referring to Figure 1, it can be understood that the axial dimension of the bearing housing 120 is equal to the axial dimension of the receiving cavity 111, and the end faces of the bearing housing 120 at both axial ends are located at the axial ends of the receiving cavity 111, that is, the bearing housing 120 covers the axial area of ​​the receiving cavity 111. This maximizes the contact area between the bearing housing 120 and the first molding compound 110, effectively improving the installation stability of the bearing housing 120.

[0039] Referring to Figures 1 and 4, it can be understood that the bearing 130 is fixedly installed in the bearing housing 121. The bearing 130 and the bearing housing 120 are interference-fitted to secure the bearing 130 to the housing 120. The bearing 130 is a sliding bearing, which has the advantages of smooth operation, reliability, and low noise, thus helping to ensure the reliable operation of the fan. Generally, the axial dimension of the bearing 130 is smaller than the axial dimension of the bearing housing 120, and the bearing 130 is entirely located within the bearing housing 121 for dust protection and lubrication.

[0040] Referring to Figure 1, it can be understood that one end of the rotating shaft 200 passes through the bearing housing 121 and is installed in the bearing 130, that is, one end of the rotating shaft 200 passes through the inner hole of the bearing 130, and there is a certain fitting clearance between the outer peripheral wall of the rotating shaft 200 and the inner peripheral wall of the inner hole of the bearing 130, so that the rotating shaft 200 can rotate relative to the bearing 130. The other end of the rotating shaft 200 extends out of the bearing housing 121 from the side opposite to the end cover 150.

[0041] Referring to Figure 4, it can be understood that, to ensure lubrication, an oil groove 133 is provided on the inner circumferential wall of the inner bore of the bearing 130. The oil groove 133 can store a certain amount of lubricating oil, thereby providing sufficient lubrication to the rotating shaft 200 so that the shaft 200 can rotate smoothly. At the same time, a dust cover 134 is provided at one axial end of the bearing 130. The dust cover 134 is located at the end of the bearing 130 away from the end cover 150. The dust cover 134 is fitted onto the shaft 200, thereby preventing dust from entering the inner bore of the bearing 130, ensuring the smooth rotation of the shaft 200 and extending the service life of the bearing 130.

[0042] Of course, the bearing 130 can also be in other structural forms, such as the bearing 130 being a rolling bearing, and the shaft 200 being fixedly connected to the inner ring of the rolling bearing.

[0043] Referring to Figure 1, it can be understood that the rotor assembly 300 is mounted on the shaft segment of the shaft 200 extending from the bearing housing 121, and the rotor assembly 300 is arranged around the outer periphery of the stator assembly 100. Specifically, the rotor assembly 300 includes a second molding compound 310 and a plurality of magnets 320, which are located on the outer periphery of the stator assembly 100 and arranged at equal intervals along the circumferential direction of the stator assembly 100. The second molding compound 310 covers the plurality of magnets 320, forming a single unit with the magnets 320. Similarly, the second molding compound 310 may completely enclose the outer periphery of the magnets 320, or the magnets 320 may have their surfaces exposed on the wall of the stator assembly 100.

[0044] Referring to Figure 1, it can be understood that the second molding body 310 includes a first end plate 311 and an annular plate 312. The first end plate 311 is generally circular in shape, and the annular plate 312 is connected to the outer edge of the first end plate 311 and extends towards the thickness direction of the first end plate 311. A through hole is provided in the middle of the first end plate 311 and it is fitted onto the shaft section of the rotating shaft 200 that extends out of the bearing chamber 121. The first end plate 311 is located on the side of the first molding body 110 opposite to the end cover 150, and the first end plate 311 is fixedly connected to the rotating shaft 200. For example, the first end plate 311 and the rotating shaft 200 are fixed by a key connection, or by a structure of mutually constraining ribs and grooves in the circumferential direction, so that the first molding body 110 and the rotating shaft 200 can rotate synchronously. The annular plate 312 is located on the side of the first end plate 311 facing the end cover 150 and is arranged around the outer periphery of the stator assembly 100, and the magnet 320 is embedded in the annular plate 312.

[0045] Referring to FIG5, it can be understood that in some embodiments, the rotor assembly 300 further includes a magnetic coil 340, which is arranged around the outer periphery of the stator assembly 100. A plurality of magnetic tiles 320 are mounted on the outer peripheral wall of the magnetic coil 340 and are arranged at equal intervals along the circumference of the stator assembly 100. The annular plate 312 of the second encapsulation 310 covers the plurality of magnetic tiles 320 and the magnetic coil 340, and the magnetic coil 340 is exposed on the annular plate 312 facing the wall of the stator assembly 100.

[0046] Therefore, under the combined action of the stator core 140 and multiple magnets 320, the rotor assembly 300 and the shaft 200 can be driven to rotate synchronously.

[0047] Referring to Figure 6, it can be understood that in some embodiments, the rotor assembly 300 includes a second molding compound 310 and a magnetic ring 330. The second molding compound 310 includes a second end plate 313, which is generally circular in shape. The second end plate 313 is located on the side of the first molding compound 110 facing away from the end cover 150, and the second end plate 313 is fixedly connected to the rotating shaft 200. The connection method between the second end plate 313 and the rotating shaft 200 can refer to the connection method between the first end plate 311 and the rotating shaft 200, and will not be repeated here. The magnetic ring 330 is installed on the side of the second end plate 313 facing the end cover 150 and arranged around the outer periphery of the stator assembly 100. For example, the magnetic ring 330 is snapped onto the second end plate 313, or the magnetic ring 330 is bonded to the second end plate 313, or the magnetic ring 330 is fixed to the second end plate 313 by screws or other fasteners. Therefore, similarly, under the combined action of the stator core 140 and the magnetic ring 330, the rotor assembly 300 and the shaft 200 can be driven to rotate synchronously.

[0048] Referring to Figure 1, it can be understood that the impeller 400 is fitted onto the shaft section of the rotating shaft 200 that extends out of the bearing chamber 121 and is located on the side of the rotor assembly 300 away from the end cover 150, with the central axis of the impeller 400 coinciding with the central axis of the rotating shaft 200. The impeller 400 is fixedly connected to the rotating shaft 200, or the impeller 400 is fixedly connected to the second encapsulated body 310, that is, the impeller 400 is fixedly connected to the side of the first end plate 311 (or the second end plate 313) away from the end cover 150. Alternatively, the impeller 400 can be fixedly connected to both the rotating shaft 200 and the second encapsulated body 310. When the impeller 400 is fixedly connected to the rotating shaft 200, the impeller 400 and the rotating shaft 200 can be fixed by a key connection, or the impeller 400 and the rotating shaft 200 can be interference-fitted. When the impeller 400 is fixedly connected to the second plastic encapsulation body 310, the impeller 400 is secured to the second plastic encapsulation body 310 by screws or other fasteners. Alternatively, the impeller 400 may also be a plastic part and integrally molded with the second plastic encapsulation body 310. The assembly of the impeller 400 and the second plastic encapsulation body 310 can be obtained through injection molding, which facilitates processing. Therefore, when the rotor assembly 300 and the rotating shaft 200 rotate, they can drive the impeller 400 to rotate, thereby achieving air delivery.

[0049] During the rotation of the impeller 400, rotor assembly 300 and shaft 200, the bearing housing 120 bears the radial force applied by the shaft 200. Conversely, the bearing housing 120 provides a reverse support force to the shaft 200 to ensure stable rotation of the shaft 200.

[0050] Typically, one end of the rotating shaft 200 is supported by the bearing housing 120 and the bearing 130, while the other end is supported by the bracket and the bearing on the bracket.

[0051] To reduce noise, the bearing housing 120 is configured as an elastic structural component, such as a rubber component, a polypropylene plastic component, or a polyethylene plastic component. When an external force is applied to the bearing housing 120, the bearing housing 120 can deform. After the external force is removed, the bearing housing 120 returns to its original shape. Therefore, the bearing housing 120 can provide a buffering effect in the radial direction, which can reduce the impact force between the bearing 130 and the first encapsulation body 110, thereby reducing noise.

[0052] The radial stiffness of bearing housing 120 is defined as k. It is easy to understand that within the radial elastic range of bearing housing 120, the radial stiffness k of bearing housing 120 is a constant value. The radial stiffness k of bearing housing 120 reflects the radial support capacity of bearing 130. The larger the radial stiffness k of bearing housing 120, the better the radial support capacity of bearing 130, and the better the rotational stability of impeller 400, rotor assembly 300 and shaft 200. Conversely, the smaller the radial stiffness k, the worse the radial support capacity of bearing 130.

[0053] Let m be the total mass of the shaft 200, rotor assembly 300, and impeller 400. Then, the total weight of the shaft 200, rotor assembly 300, and impeller 400 is mg, where g is the acceleration due to gravity. Generally, in the operating environment, the shaft 200 of the fan is arranged horizontally, and the bearing 130 and bearing housing 120 need to bear the gravity of the shaft 200, rotor assembly 300, and impeller 400 in the radial direction.

[0054] Let U be the imbalance (i.e., the dynamic imbalance) of the shaft 200, rotor assembly 300, and impeller 400, and let ω be the maximum angular velocity of the rotor assembly 300. Due to manufacturing errors, and because the total mass distribution of the shaft 200, rotor assembly 300, and impeller 400 is uneven and deviates from the rotation axis, an imbalance inevitably exists in the rotating system of the shaft 200, rotor assembly 300, and impeller 400. During rotation, this imbalance manifests as centrifugal force, the magnitude of which is Uω. 2 This centrifugal force is applied to bearing 130 and bearing housing 120. Excessive imbalance can cause the rotation axis of the rotating system of shaft 200, rotor assembly 300 and impeller 400 to deviate from the central axis of stator assembly 100, resulting in a rutting failure.

[0055] Generally, to minimize the imbalance, a mass block is installed on the outer wall of the wind turbine 400 to make the imbalance approach zero. Let the radius of the wind turbine 400 be r1, and the mass of the mass block installed on its outer wall be m1. When r1m1 = U, the imbalance is zero. The value of the imbalance U can be directly measured using equipment such as a dynamic balancing instrument.

[0056] The radial stiffness of bearing housing 120 is k, the total mass of shaft 200, rotor assembly 300 and impeller 100 is m, the unbalance of shaft 200, rotor assembly 300 and impeller 400 is U, and the maximum angular velocity of rotor assembly 300 is ω, satisfying the following:

[0057] Understandable, This can be understood as the radial force borne by the bearing housing 120 during the rotation of the rotating system consisting of the shaft 200, rotor assembly 300, and impeller 400. Therefore, This can be understood as the ratio of the radial force borne by the bearing housing 120 to its radial stiffness being greater than 0 and less than or equal to 0.315. In other words, when selecting materials for the bearing housing 120, the radial stiffness k of the bearing housing 120 is determined based on the total weight and unbalance of the rotating system of the shaft 200, rotor assembly 300, and impeller 400, and satisfies...

[0058] make exist Given a fixed value, a larger radial stiffness k of the bearing housing 120 increases the structural stiffness of the bearing housing 120, enabling it to withstand the radial forces applied by the shaft 200, rotor assembly 300, and impeller 400. This provides stable radial support to the shaft 200, rotor assembly 300, and impeller 400, improving their rotational stability and ensuring their rotational accuracy. Even in high-temperature and high-humidity environments, the bearing housing 120 can provide stable support, thereby reducing the risk of rotor rubbing failure in the motor assembly, effectively improving the fan's operational stability, and reducing vibration and noise.

[0059] It is easy to understand that when the radial unilateral force on the bearing housing 120, which satisfies the above parameter relationship, is 19N, the radial unilateral deformation of the bearing housing 120 is less than 1mm.

[0060] Referring to Figures 1 to 3, it can be understood that the first molding compound 110 engages with the bearing housing 120 to form a constraint in the axial direction. Specifically, the first molding compound 110 includes a first engaging portion 112, which is a protrusion disposed on the inner peripheral wall of the receiving cavity 111, i.e., the protrusion extends radially out of the inner peripheral wall of the receiving cavity 111. The protrusion can be annular or arc-shaped. The first engaging portion 112 is located at one end of the receiving cavity 111 near the end cap 150. Correspondingly, the bearing housing 120 includes a second engaging portion 122, which is a recess disposed on the outer peripheral wall of the bearing housing 120, i.e., the recess is radially recessed relative to the outer peripheral wall of the bearing housing 120. Similarly, the recess can be annular or arc-shaped, and when the protrusion is annular, the recess is also annular. The protrusion is accommodated in the concave portion, thereby forming an axial constraint between the protrusion and the concave portion. That is, the first plastic seal 110 and the bearing housing 120 form an axial constraint, which can prevent the bearing housing 120 from moving axially relative to the first plastic seal 110, thus restricting the axial degree of freedom of the bearing housing 120 and improving the installation stability of the bearing housing 120.

[0061] Since the bearing housing 120 is an elastic structural component with a certain deformation, when installing the bearing housing 120, the bearing housing 120 can be pressed into the receiving cavity 111 from the opening on the side away from the end cover 150. At the position of the protrusion, the bearing housing 120 is deformed by compression. As the bearing housing 120 is further pressed in, the installation of the bearing housing 120 is completed when the protrusion is accommodated in the concave part, which facilitates assembly.

[0062] Of course, the first snap-fit ​​portion 112 can be a recess, and the second snap-fit ​​portion 122 can be a convex portion that can be accommodated in the recess. That is, the positions of the convex portion and the recess on the first plastic seal 110 and the bearing seat 120 can be interchanged, which will not be elaborated here.

[0063] Referring to Figure 3, it can be understood that a guide portion 123 is provided at one end of the bearing housing 120 along the axial direction. Specifically, the guide portion 123 is provided on the outer peripheral wall of the bearing housing 120 and located at the end of the bearing housing 120 facing the end cover 150. The guide portion 123 has a beveled or arcuate structure, and its outer diameter decreases along the axial direction and close to the end cover 150. Therefore, when installing the bearing housing 120, the guide portion 123 first abuts against the protrusion. As the bearing housing 120 is further pressed in, the guide portion 123 guides the end of the bearing housing 120 to insert into the space on the side of the protrusion facing the central axis of the receiving cavity 111. The bearing housing 120 is deformed by compression until the protrusion is accommodated in the recess. In this way, by providing the guide portion 123, the bearing housing 120 can be easily deformed under the compression of the protrusion, making it easier for the protrusion to be accommodated in the recess, thus facilitating installation.

[0064] Referring to Figures 3 and 4, it can be understood that the bearing housing 121 includes an arc-shaped inner wall 1211, which is annular and recessed radially toward the outer peripheral wall of the bearing seat 120. Correspondingly, the bearing 130 includes an arc-shaped outer wall 131, which protrudes radially toward the arc-shaped inner wall 1211, and the arc-shaped outer wall 131 matches and abuts against the arc-shaped inner wall 1211. Therefore, when installing the bearing 130, the bearing 130 can be adjusted by swinging along the arc-shaped inner wall 1211 so that the central axis of the bearing 130 coincides as much as possible with the central axis of the stator assembly 100, thereby improving the installation accuracy. At the same time, after the bearing 130 is pressed into the bearing housing 121, a certain constraint is formed between the bearing seat 120 and the bearing 130 in both axial directions at the arc-shaped inner wall 1211, thereby preventing the bearing 130 from shifting axially relative to the bearing seat 120, which is beneficial to improving the installation stability of the bearing 130.

[0065] Referring to Figures 3 and 4, it can be understood that the bearing housing 121 includes a first end face 1212 perpendicular to the axial direction. The first end face 1212 is located at the end of the arc-shaped inner wall 1211 axially close to the end cover 150, i.e., the first end face 1212 faces the impeller 400. Correspondingly, the bearing 130 includes a second end face 132, located at the end of the bearing 130 axially away from the impeller 400. After the bearing 130 is installed in the bearing housing 121, the second end face 132 abuts against the first end face 1212. Therefore, when installing the bearing 130, the bearing seat 120 can use the first end face 1212 to position the bearing 130 axially, facilitating installation and ensuring that the bearing 130 is installed in place, i.e., ensuring that the arc-shaped outer wall 131 abuts against the arc-shaped inner wall 1211, preventing the bearing 130 from becoming loose.

[0066] The air handling device of the second aspect of this application includes the fan of the first aspect of this application. The air handling device may be an air conditioner, a evaporative cooler, an air purifier, a humidifier, etc. The fan is part of the air outlet device of the air handling device and is used to make air flow to form wind, which will not be described in detail here.

[0067] Since the air handling equipment adopts all the technical solutions of the fan in the above embodiments, it has at least all the beneficial effects brought about by the technical solutions in the above embodiments.

[0068] The embodiments of this application have been described in detail above with reference to the accompanying drawings. However, this application is not limited to the above embodiments. Within the scope of knowledge possessed by those skilled in the art, various changes can be made without departing from the spirit of this application.

Claims

1. Fan, including: A stator assembly includes a stator body, a bearing housing, and a bearing. The stator body has a receiving cavity, the bearing housing is installed in the receiving cavity, the bearing housing has a bearing chamber, and the bearing is fixedly installed in the bearing chamber. A rotating shaft passes through the bearing chamber and is installed in the bearing; A rotor assembly is mounted on the shaft and arranged around the outer periphery of the stator assembly; as well as The impeller is located on one side of the rotor assembly along the axial direction and is mounted on the shaft; Wherein, the bearing housing is an elastic structural component, the radial stiffness of the bearing housing is k, the total mass of the shaft, the rotor assembly, and the wind turbine is m, the imbalance of the shaft, the rotor assembly, and the wind turbine is U, and the maximum angular velocity of the rotor assembly is ω, satisfying: g is the acceleration due to gravity.

2. The fan according to claim 1, wherein, The stator body and the bearing housing are interference fit.

3. The fan according to claim 1 or 2, wherein, The stator body includes a first snap-fit ​​portion, and the bearing housing includes a second snap-fit ​​portion. The second snap-fit ​​portion engages with the first snap-fit ​​portion to restrict the axial degree of freedom of the bearing housing.

4. The fan according to claim 3, wherein, The first snap-fit ​​portion is a protrusion protruding from the inner peripheral wall of the receiving cavity, and the second snap-fit ​​portion is a recessed portion recessed relative to the outer peripheral wall of the bearing seat, wherein the protrusion is received in the recess.

5. The fan according to claim 4, wherein, One end of the bearing housing is provided with a guide portion, which is used to guide the protrusion into the recess.

6. The fan according to any one of claims 1 to 5, wherein, The bearing housing includes an arc-shaped inner wall that is recessed toward the outer peripheral wall of the bearing seat along the radial direction of the rotating shaft. The bearing includes an arc-shaped outer wall that protrudes toward the arc-shaped inner wall along the radial direction of the rotating shaft, and the arc-shaped outer wall abuts against the arc-shaped inner wall.

7. The fan according to claim 6, wherein, The bearing housing includes a first end face perpendicular to the axial direction, the first end face facing the wind turbine, and the bearing includes a second end face located at one end along the axial direction, the second end face abutting against the first end face.

8. The fan according to any one of claims 1 to 7, wherein, The rotor assembly includes a second molding body and a plurality of magnets. The second molding body includes a first end plate and an annular plate connected to one side of the first end plate along the axial direction. The plurality of magnets are mounted on the annular plate and arranged at circumferential intervals along the stator assembly. The impeller is connected to the other side of the first end plate along the axial direction.

9. The fan according to any one of claims 1 to 8, wherein, The rotor assembly includes a second encapsulated body and a magnetic ring. The second encapsulated body includes a second end plate. The magnetic ring is mounted on one side of the second end plate along the axial direction and arranged around the outer periphery of the stator assembly. The impeller is connected to the other side of the second end plate along the axial direction.

10. The fan according to claim 8 or 9, wherein, The second molding body and the wind turbine are integrally molded parts.

11. An air handling apparatus, comprising the fan as described in any one of claims 1 to 10.

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