CN114658676B

CN114658676B - Fan and cleaning equipment

Info

Publication number: CN114658676B
Application number: CN202210411246.2A
Authority: CN
Inventors: 杨帆; 龚涛; 杨志鹏; 吴昕耿; 曹红军; 张肃
Original assignee: Guangdong Meizhi Compressor Co Ltd
Current assignee: Guangdong Meizhi Compressor Co Ltd
Priority date: 2022-04-19
Filing date: 2022-04-19
Publication date: 2023-06-23
Anticipated expiration: 2042-04-19
Also published as: CN114658676A

Abstract

The invention discloses a fan and cleaning equipment, and relates to the technical field of fan equipment, wherein the fan comprises a shell, a shaft sleeve and a rotor system, the shaft sleeve is fixed on the shell, the rotor system comprises an impeller, a main shaft, a first thrust disc, a second thrust disc and a rotor, the main shaft is rotationally arranged in the shaft sleeve and is in clearance fit with the shaft sleeve to form a radial bearing, friction force between the main shaft and the shaft sleeve is reduced, the impeller and the rotor are respectively fixed at two ends of the main shaft, the first thrust disc and the second thrust disc are respectively fixed on the main shaft and are in clearance fit with two ends of the shaft sleeve, so that two thrust bearings with opposite acting force directions are formed, under the maximum rotating speed of the fan, the thrust forces of the two thrust bearings are designed to be 1.2-2 times of the sum of the maximum value of the gravity of the axial gas force of the rotor system and the impeller, the stable operation of the rotor system can be ensured, and the stable operation under the highest rotating speed can be realized under various orientations, the performance and the mechanical noise of the fan are improved, and the stability and the highest rotating speed of the fan are improved.

Description

Fan and cleaning equipment

Technical Field

The invention relates to the technical field of fan equipment, in particular to a fan and cleaning equipment.

Background

The fan for the dust collector generates negative pressure at the inlet of the fan through the rotation of the impeller, thereby generating suction force for dust and the like. The rotating shaft of the traditional impeller is generally supported by adopting a ball bearing, but mechanical friction can be generated when the ball bearing runs, and particularly, the mechanical friction of the ball bearing is more obvious after the rotating speed of the impeller is increased, so that the mechanical efficiency is obviously reduced, abnormal vibration and noise can be generated, and the service life of the ball bearing is shortened.

In the related art, the fan adopts a gas bearing consisting of a radial bearing and a thrust bearing to replace a ball bearing, but as various use conditions exist in the use process of the fan, the supporting effect of the gas bearing on the rotor system when the rotor system runs in any direction directly influences the rotating speed of the rotor system, so that whether the fan can reach the highest running speed is influenced.

Disclosure of Invention

The present invention aims to solve at least one of the technical problems existing in the prior art. Therefore, the invention provides the fan, which can ensure that the fan can stably reach the requirement of the highest running speed in any direction.

The invention further provides cleaning equipment with the fan.

According to an embodiment of the first aspect of the present invention, a fan includes: a shell provided with a supporting frame; the shaft sleeve is fixed on the supporting frame; the rotor system comprises an impeller, a main shaft, a first thrust disc, a second thrust disc and a rotor, wherein the main shaft is rotationally arranged in a shaft sleeve, part of the outer peripheral wall of the main shaft is in clearance fit with the inner peripheral wall of the shaft sleeve, the impeller is fixed at one end of the main shaft, the rotor is fixed at the other end of the main shaft, the first thrust disc is fixed at the main shaft and in clearance fit with the shaft sleeve, one end of the first thrust disc, which faces the shaft sleeve, is provided with a first end wall, the opposite end wall of the first end wall or the shaft sleeve is provided with a plurality of first grooves, the first grooves are arranged at intervals along the circumferential direction of the main shaft, the second thrust disc is fixed at the main shaft and in clearance fit with the shaft sleeve, one end of the second thrust disc, which faces the shaft sleeve, is provided with a second end wall, the second end wall or the shaft sleeve A plurality of second grooves are formed in the opposite end walls of the spindle, and the second grooves are arranged at intervals along the circumferential direction of the spindle; a stator which is arranged around the periphery of the rotor; the gravity of the rotor system is G, the diameter of an air suction port of the impeller is D11, and the maximum outer diameter of the impeller is D12; the maximum vacuum degree of the fan is P, under the maximum rotating speed of the fan, the thrust of the first thrust disc is F1, and the thrust of the second thrust disc is F2, so that the requirements are satisfied: F1/(G+P (pi D12) of 1.2 ² /4-πD11 ² (4))is less than or equal to 2, and F2/(G+P (pi D12) is less than or equal to 1.2 ² /4-πD11 ² /4））≤2。

The fan provided by the embodiment of the invention has at least the following beneficial effects:

the radial bearing provides radial bearing force for the rotor system so that the main shaft is separated from the shaft sleeve when rotating at high speed, and friction force between the main shaft and the shaft sleeve is reduced; the first thrust disc and the second thrust disc are fixed on the main shaft and form two thrust bearings with opposite acting force directions with the shaft sleeve respectively, under the maximum rotating speed of the fan, the thrust forces of the two thrust bearings are designed to be the sum of the maximum values of the gravity of the rotor system and the axial gas force of the impeller, which is 1.2-2 times, so that the shaft sleeve can be ensured to be separated from the first thrust disc and the second thrust disc, the stability of the rotor system in the axial direction is improved, the influence of the fan on the running of the rotor system when the fan works in any direction is reduced, the deflection of the rotor system is effectively reduced, the rotor system can stably run at the highest rotating speed under various using conditions, and the requirements of miniaturization and light weight of the fan are simultaneously ensured; by adopting the gas bearing to reduce the friction of the rotor system, the running of the rotor system can be more stable, the performance and mechanical noise of the fan are improved, and the stability and the highest rotating speed of the fan are improved.

According to some embodiments of the invention, 1.4.ltoreq.F1/(G+P (pi D12) ² /4-πD11 ² (4))/(1.6, and 1.4. Ltoreq.F2/(G+P (. Pi.D12) ² /4-πD11 ² /4））≤1.6。

According to some embodiments of the invention, a plurality of the first grooves are provided in the first end wall, the first grooves extend toward the axis of the spindle and the extending direction is inclined in a direction opposite to a rotation direction around the first thrust plate.

According to some embodiments of the invention, an end of the first groove remote from the axis is located at a peripheral edge of the first end wall.

According to some embodiments of the invention, the first grooves have the same structure and form a first reference circle toward one end of the axis, the diameter of the first reference circle is D21, the number of the first grooves is n, and the width of the first grooves on the first reference circle is B, so that: nB/pi D21 is more than or equal to 20% and less than or equal to 65%.

According to some embodiments of the invention, the first groove includes a first outer profile and a first inner profile sequentially arranged along a rotation direction of the first thrust disc, a tangential angle of the first outer profile at an outer peripheral edge of the first end wall is λ1, satisfying: lambda 1 is more than or equal to 45 degrees and less than or equal to 80 degrees.

According to some embodiments of the invention, the first groove is a chute or a spiral groove.

According to some embodiments of the invention, the first end wall or the opposite end wall of the shaft sleeve is provided with a plurality of first connecting grooves, and the first connecting grooves are respectively connected to one ends of the first grooves facing the axis in a corresponding manner and are bent relative to the first grooves.

According to some embodiments of the invention, the first groove is formed by laser machining, etching machining or electric spark machining.

According to some embodiments of the invention, the main shaft comprises a shaft neck and a shaft body, the diameter of the shaft neck is larger than that of the shaft body, the first thrust disk is sleeved on the shaft body and is abutted with one end of the shaft neck, which faces the impeller, and the second thrust disk is sleeved on the shaft body and is abutted with one end of the shaft neck, which is far away from the impeller.

According to some embodiments of the invention, the length of the bushing is less than the length of the journal and the difference is 8 μm to 16 μm.

According to some embodiments of the invention, the journal has an outer diameter D31, the ends of the first grooves facing the axis of the spindle form a first reference circle, the diameter of the first reference circle is D21, and the outer diameter of the sleeve is D41, satisfying: d21 Not less than D31 and D21 not more than D41.

According to some embodiments of the invention, the journal has an outer diameter D31 and the shaft has an outer diameter D32, satisfying: D32/D31 is more than or equal to 40% and less than or equal to 80%, and D32 is more than or equal to 4mm.

According to some embodiments of the invention, the second thrust disk is annular, the outer diameter of the second thrust disk is D22, the inner diameter of the stator is D51, and the outer diameter of the journal is D31, satisfying: 1.3D31D 22 is less than or equal to 0.98D51.

According to some embodiments of the invention, the length of the journal is L0 and the length of the spindle is L, satisfying: l0 is more than or equal to 0.2L and less than or equal to 0.8L.

According to some embodiments of the invention, the outer peripheral wall of the journal is in clearance fit with the inner peripheral wall of the sleeve, one of the outer peripheral wall of the journal and the inner peripheral wall of the sleeve is provided with a plurality of third grooves, and the third grooves are arranged at intervals along the circumferential direction of the spindle.

According to some embodiments of the invention, the inner diameter of the bushing is greater than the outer diameter of the journal by a difference of 4 μm to 10 μm.

According to some embodiments of the invention, the plurality of third grooves are arranged on the outer peripheral wall of the journal and extend spirally along the axial direction of the main shaft, and the outer peripheral wall of the journal is further provided with third connecting grooves which are connected to one end of the third grooves far away from the end wall of the journal and are bent relative to the third grooves.

According to some embodiments of the invention, one end of the third groove is located at one of the end walls of the journal.

According to some embodiments of the invention, one of the outer peripheral wall of the journal and the inner peripheral wall of the sleeve is provided with a plurality of groove groups, the plurality of groove groups are arranged at intervals along the axial direction of the journal, and each groove group comprises a plurality of third grooves uniformly distributed along the circumferential direction of the journal.

According to some embodiments of the invention, along the axial direction of the spindle, the total length of the plurality of groove groups is L1, and the length of the journal is L0, satisfying: L1/L0 is more than or equal to 50% and less than or equal to 98%.

According to some embodiments of the invention, the first end wall is annular, conical or spherical.

A cleaning apparatus according to an embodiment of the second aspect of the invention comprises a blower as described in the above embodiments.

The cleaning device provided by the embodiment of the invention has at least the following beneficial effects:

the fan of the embodiment of the first aspect is adopted, the fan is fixed on the supporting frame of the shell through the shaft sleeve, and the rotor system comprises the impeller, the main shaft, the first thrust disk, the second thrust disk and the rotor, wherein the main shaft is rotationally arranged in a radial bearing formed by the shaft sleeve, and the radial bearing provides radial bearing force for the rotor system to enable the main shaft to be separated from the shaft sleeve when the main shaft rotates at a high speed, so that the friction force between the main shaft and the shaft sleeve is reduced; the first thrust disc and the second thrust disc are fixed on the main shaft and form two thrust bearings with opposite acting force directions with the shaft sleeve respectively, under the maximum rotating speed of the fan, the thrust forces of the two thrust bearings are designed to be the sum of the maximum values of the gravity of the rotor system and the axial gas force of the impeller, which is 1.2-2 times, so that the shaft sleeve can be ensured to be separated from the first thrust disc and the second thrust disc, the stability of the rotor system in the axial direction is improved, the influence of the fan on the running of the rotor system when the fan works in any direction is reduced, the deflection of the rotor system is effectively reduced, the rotor system can stably run at the highest rotating speed under various using conditions, and the requirements of miniaturization and light weight of the fan are simultaneously ensured; by adopting the gas bearing to reduce the friction of the rotor system, the running of the rotor system can be more stable, the performance and mechanical noise of the fan are improved, and the stability and the highest rotating speed of the fan are improved.

Additional aspects and advantages of the invention 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 the invention.

Drawings

The invention is further described with reference to the accompanying drawings and examples, in which:

FIG. 1 is a schematic cross-sectional view of a blower according to one embodiment of the invention;

FIG. 2 is an exploded view of a blower according to an embodiment of the present invention;

FIG. 3 is a schematic cross-sectional view of a rotor system according to one embodiment of the present disclosure;

FIG. 4 is an exploded schematic view of a rotor system according to one embodiment of the present invention;

FIG. 5 is a schematic bottom view of one embodiment of the first thrust plate of FIG. 4;

FIG. 6 is a schematic bottom view of another embodiment of the first thrust plate of FIG. 4;

FIG. 7 is a schematic bottom view of another embodiment of the first thrust plate of FIG. 4;

FIG. 8 is a schematic bottom view of another embodiment of the first thrust plate of FIG. 4;

FIG. 9 is a schematic front view of the spindle of FIG. 4;

FIG. 10 is a cross-sectional view of the bushing of FIG. 2;

FIG. 11 is a schematic cross-sectional view of a blower according to another embodiment of the invention;

FIG. 12 is a schematic cross-sectional view of a blower in accordance with another embodiment of the invention.

Reference numerals:

a blower 1000;

a fan housing 100; an air inlet channel 110;

An impeller 200;

a first diffuser 300; a first diffuser 310;

a housing 400; a support frame 410; a mounting hole 411; a second diffuser 420; a second diffuser 421; rib 430;

a main shaft 500; journal 510; a third groove 511; a third connecting groove 512; groove group 513; a shaft body 520; a first thrust plate 530; a first end wall 531; a first groove 532; a first connection groove 533; a second thrust plate 540; a second end wall 541; a second groove 542;

a sleeve 600;

a stator 700;

a rotor 800;

an electronic control board 900.

Detailed Description

Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are illustrative only and are not to be construed as limiting the invention.

In the description of the present invention, it should be understood that the direction or positional relationship indicated with respect to the description of the orientation, such as up, down, etc., is based on the direction or positional relationship shown in the drawings, is merely for convenience of describing the present invention and simplifying the description, and does not indicate or imply that the apparatus or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the present invention.

In the description of the present invention, plural means two or more. The description of the first and second is for the purpose of distinguishing between technical features only and should not be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated or implicitly indicating the precedence of the technical features indicated.

In the description of the present invention, unless explicitly defined otherwise, terms such as arrangement, installation, connection, etc. should be construed broadly and the specific meaning of the terms in the present invention can be reasonably determined by a person skilled in the art in combination with the specific contents of the technical scheme.

Referring to fig. 1 and 2, a blower 1000 according to an embodiment of the present invention may be applied to a product requiring an ultra-high speed blower, such as a vacuum cleaner. The rotating speed of the ultra-high speed fan of the dust collector is generally over 10 ten thousand revolutions, reaching 11 ten thousand revolutions or even 13 ten thousand revolutions. Traditional fan adopts ball bearing to support, but ball bearing can produce mechanical friction when the superhigh speed operation for ball bearing's wearing and tearing, reduce mechanical efficiency, still can produce unusual vibration and noise to make ball bearing's life-span show and shorten. Therefore, the embodiment of the invention adopts the gas bearing to replace the ball bearing, thereby improving the stability of the fan in the ultra-high speed running process.

Referring to fig. 1 and 2, a fan 1000 according to an embodiment of the present invention includes a fan housing 100, an impeller 200, a first diffuser 300, a casing 400, a main shaft 500, and a shaft housing 600. The casing 400 includes a support frame 410, the support frame 410 is located at the center of the casing 400, the support frame 410 is provided with a mounting hole 411, the shaft sleeve 600 is fixedly mounted in the mounting hole 411, and the spindle 500 is rotatably disposed in the shaft sleeve 600. It should be appreciated that the sleeve 600 may be fixed to the support frame 410 by an adhesive manner, or may be fixed by an interference fit, a clamping connection, welding, an integral molding manner, etc., which is not limited herein.

Referring to fig. 1 and 2, it can be appreciated that the impeller 200 is fixedly coupled to the upper end of the main shaft 500, and the impeller 200 is drivingly coupled through the main shaft 500. The fan housing 100 is covered on the outer periphery of the impeller 200, the fan housing 100 and the first diffuser 300 are fixedly connected to the casing 400, and the first diffuser 300 is arranged between the impeller 200 and the supporting frame 410. An air inlet channel 110 is formed between the impeller 200 and the fan housing 100, a first diffusion channel 310 is formed between the first diffuser 300 and the fan housing 100, and the first diffusion channel 310 is communicated with the air inlet channel 110. The impeller 200 rotates to form an air flow, and the kinetic energy of the air flow increases after the air flow passes through the air inlet channel 110. After the airflow continues to enter the first diffusion channel 310, the first diffusion channel 310 converts kinetic energy of the airflow into pneumatic energy, so that the pressure of the airflow is increased, the airflow after being diffused is blown farther, the efficiency of the fan 1000 is increased, and the suction force of the fan 1000 is stronger.

Referring to fig. 2, it can be understood that the casing 400 further includes a second diffuser 420, the second diffuser 420 surrounds the outer periphery of the support frame 410, and the support frame 410 is fixedly connected with the second diffuser 420 through a rib 430, so that the connection of the support frame 410 is more stable. The second diffuser 420 forms a second diffuser passage 421, and the second diffuser passage 421 communicates with the first diffuser passage 310. After the airflow of the first diffusion channel 310 is further diffused by the second diffusion channel 421, the diffusion effect can be improved, and the noise reduction of the fan 1000 is facilitated.

Referring to fig. 2, the fan 1000 of the embodiment of the present invention further includes a stator 700, a rotor 800, and an electric control board 900. The rotor 800 is mounted to a lower end of the main shaft 500, i.e., an end of the main shaft 500 remote from the impeller 200. The stator 700 is fixed to the casing 400, the stator 700 is disposed around the outer circumference of the rotor 800, and the stator 700 and the rotor 800 cooperate to drive the spindle 500 to rotate, thereby driving the impeller 200 to rotate. An electric control board 900 is mounted to the stator 700 or the casing 400, and the electric control board 900 is used for controlling the fan 1000.

Referring to fig. 3, it can be appreciated that the impeller 200, the main shaft 500, the first thrust plate 530, the second thrust plate 540, and the rotor 800 constitute a rotor system. The spindle 500 includes a journal 510 and a shaft body 520, and an outer diameter size of the journal 510 is larger than an outer diameter size of the shaft body 520. The main shaft 500 is rotationally arranged in the shaft sleeve 600, the outer peripheral wall of the shaft neck 510 is in clearance fit with the inner peripheral wall of the shaft sleeve 600, the main shaft 500 is rotationally arranged in a radial bearing formed by the shaft sleeve 600 through the shaft neck 510, the main shaft 500 and the radial bearing are in clearance fit along the radial direction of the main shaft 500, the radial clearance is a tiny clearance, the radial bearing provides radial bearing force for the shaft neck 510, and further provides radial bearing force for a rotor system, so that the main shaft 500 is separated from the shaft sleeve 600 when rotating at high speed, and friction force between the main shaft 500 and the shaft sleeve 600 is reduced. In addition, the spindle 500 of the present embodiment can effectively increase the contact area between the spindle 500 and the radial bearing by increasing the diameter of the journal 510, and improve the supporting effect of the radial bearing on the spindle 500.

Referring to fig. 1 and 3, it can be appreciated that the second thrust disk 540 is annular, the second thrust disk 540 is close to the stator 700, in order to reduce interference between the second thrust disk 540 and the stator 700, by defining the outer diameter of the second thrust disk 540 as D22, the inner diameter of the stator 700 as D51, the outer diameter of the journal 510 as D31, and the following: 1.3D31D 22 is less than or equal to 0.98D51. More preferably 1.4D31.ltoreq.D22.ltoreq. 0.95D51 is defined. In addition, the embodiment of the invention can lead the mass distribution of the whole rotor system to be more uniform through the proportion parameters, and effectively improve the running stability of the fan 1000.

Referring to fig. 4, it is understood that the outer circumferential wall of the journal 510 is provided with a plurality of third grooves 511, and the plurality of third grooves 511 are uniformly distributed along the circumferential direction of the spindle 500, although the plurality of third grooves 511 may be alternatively arranged. The plurality of third grooves 511 may have a spiral groove, a chute, or the like. It will be appreciated that an air gap is formed between the outer circumferential wall of the journal 510 and the inner circumferential wall of the sleeve 600, and during the high-speed rotation of the main shaft 500, air enters the air gap and forms a local high-pressure region in the third groove 511, and the pressure generated by the local high-pressure region generates a radial bearing force on the rotor system, so that the journal 510 is completely separated from the sleeve 600, the rotor system is more stable during the high-speed operation, and the performance and mechanical noise of the fan 1000 are further improved.

As another embodiment, a plurality of third grooves 511 may be provided in the inner circumferential wall of the sleeve 600. When the main shaft 500 rotates at a high speed, air can enter the air gap and form a local high pressure area in the third groove 511, and the pressure generated by the local high pressure area generates radial bearing force on the rotor system, so that the journal 510 is completely separated from the shaft sleeve 600, the rotor system is more stable during high-speed operation, and the performance and mechanical noise of the fan 1000 are further improved.

Referring to fig. 4, it may be understood that the first thrust plate 530 and the second thrust plate 540 may be respectively sleeved and fixed on the shaft body 520 at two ends of the journal 510, and the first thrust plate 530 and the second thrust plate 540 implement positioning and installation through two shoulders (not shown in the drawing) formed at the connection part of the journal 510 and the shaft body 520. For example, the first thrust plate 530 and the second thrust plate 540 may be fixed to the shaft 520 by gluing, interference fit, welding, or the like.

It will be appreciated that the first thrust disc 530 is in clearance fit with the shaft sleeve 600, the axial gap between the first thrust disc 530 and the shaft sleeve 600 is a small gap, the end of the first thrust disc 530 facing the shaft sleeve 600 is provided with a first end wall 531, the first end wall 531 is provided with a plurality of first grooves 532, and the plurality of first grooves 532 are arranged at intervals along the circumference of the main shaft 500, so that during the high-speed rotation of the first thrust disc 530, air enters the air gap and forms a local high-pressure area in the first grooves 532, and the pressure generated by the local high-pressure area generates an axial first thrust force on the rotor system, thereby forming the thrust bearing function. As another example, a plurality of first grooves 532 may be provided on an end wall of the sleeve 600 opposite to the first end wall 531, and when the first thrust plate 530 rotates at a high speed, air may enter the air gap and form a local high pressure area in the first grooves 532, and the pressure generated by the local high pressure area generates a first thrust force on the rotor system in the axial direction.

It may be appreciated that the second thrust disc 540 is in clearance fit with the shaft sleeve 600, an axial gap existing between the second thrust disc 540 and the shaft sleeve 600 is a small gap, one end of the second thrust disc 540 facing the shaft sleeve 600 is provided with a second end wall 541, the second end wall 541 is provided with a plurality of second grooves 542, and the plurality of second grooves 542 are arranged at intervals along the circumference of the main shaft 500, so that during the high-speed rotation of the second thrust disc 540, air enters the air gap and forms a local high-pressure area in the second grooves 542, and pressure generated by the local high-pressure area generates an axial second thrust force on the rotor system, thereby forming the thrust bearing function. The second thrust force is opposite to the first thrust force. As another embodiment, a plurality of second grooves 542 may be further formed on an end wall of the sleeve 600 opposite to the second end wall 541, and when the second thrust plate 540 rotates at a high speed, air may enter the air gap and form a local high pressure area in the second grooves 542, where the pressure generated by the local high pressure area generates a second thrust force on the rotor system in the axial direction.

It can be appreciated that under the interaction of the first thrust force and the second thrust force, the shaft sleeve 600 can be ensured to be separated from the first thrust disk 530 and the second thrust disk 540, friction between the shaft sleeve 600 and the first thrust disk 530 and the second thrust disk 540 is reduced, and the rotor system is subjected to stable axial bearing force, so that the running stability of the rotor system is improved.

Referring to fig. 3, the gravity of the rotor system is defined as G, the suction port diameter of the impeller 200 is D11, and the maximum outer diameter of the impeller 200 is D12. It will be appreciated that the suction port of the impeller 200 is located at the upper end of the impeller 200, and the maximum outer diameter of the impeller 200 is located at the positionAt the lower end of the impeller 200, the weight G of the rotor system, the diameter D11 of the suction opening of the impeller 200, and the maximum outer diameter D12 of the impeller 200 can be directly measured. Defining the maximum vacuum degree of the blower 1000 as P, at the maximum rotation speed of the blower 1000, the first thrust force is F1, and the second thrust force is F2, where it should be noted that the blower 1000 is used as a core component of a cleaning device (e.g., a dust collector), and the maximum rotation speed of the blower 1000 may be understood as a rotation speed corresponding to the cleaning device when the cleaning device is operated in the maximum gear. It will be appreciated that the maximum vacuum level P of the blower 1000 is a parameter that can be obtained on the nameplate of the blower 1000. The maximum vacuum degree P of the limit working condition corresponds to the maximum value Fn of the axial gas force of the impeller 200, and the maximum value Fn=P (pi D12) of the axial gas force of the impeller 200 can be calculated by providing the parameters ² /4-πD11 ² (4); the first thrust force F1 and the second thrust force F2 may be acquired by a pressure sensor.

In order to improve the stability of the rotor system and enable the fan 1000 to stably reach the requirement of the highest speed in any direction, the fan 1000 of the embodiment of the invention designs the first thrust force F1 to be larger than or equal to 1.2 times of the sum value of the gravity G of the rotor system and the maximum value Fn of the axial gas force of the impeller 200, and smaller than or equal to 2 times of the sum value of the gravity G of the rotor system and the maximum value Fn of the axial gas force of the impeller 200; the second thrust force F2 is designed to be greater than or equal to 1.2 times the sum of the gravity G of the rotor system and the maximum value Fn of the axial gas force of the impeller 200 and less than or equal to 2 times the sum of the gravity G of the rotor system and the maximum value Fn of the axial gas force of the impeller 200.

The fan 1000 of the embodiment of the invention is limited by the above parameters, so that the first thrust force F1 and the second thrust force F2 are not obviously influenced by the gravity G of the rotor system and the maximum value Fn of the axial gas force of the impeller 200, and when the fan 1000 works in any direction, the rotor system can be supported under the action of the first thrust force F1 and the second thrust force F2, thereby ensuring that the shaft sleeve 600 can be separated from the first thrust disc 530 and the second thrust disc 540, reducing the influence of the fan 1000 on the operation of the rotor system when working in any direction, effectively reducing the deflection of the rotor system, improving the stability of the rotor system in the axial direction, and enabling the rotor system to stably operate at the highest rotation speed under various working conditions. It can be appreciated that the first thrust force F1 and the second thrust force F2 should not be too large, and when the first thrust force F1 and the second thrust force F2 are too large, the outer diameters of the shaft sleeve 600, the first thrust plate 530 and the second thrust plate 540 need to be increased, so that the weight of the rotor system is increased greatly, and the assembly gap between the shaft sleeve 600 and the first thrust plate 530 and the second thrust plate 540 needs to be reduced excessively, so that the assembly precision requirement is improved, and the assembly difficulty is increased; the requirements for miniaturization and weight reduction of the blower 1000 cannot be satisfied.

According to the embodiment of the invention, the friction of the rotor system is reduced by adopting the gas bearing formed by the radial bearing and the two thrust bearings, so that the running of the rotor system is more stable, the performance and mechanical noise of the fan 1000 are improved, and the stability and the highest rotating speed of the fan 1000 are improved.

It can be appreciated that the fan 1000 according to the embodiment of the present invention designs the first thrust force F1 to be greater than or equal to 1.4 times the sum of the gravity G of the rotor system and the maximum value Fn of the axial gas force of the impeller 200, and to be less than or equal to 1.6 times the sum of the gravity G of the rotor system and the maximum value Fn of the axial gas force of the impeller 200; the second thrust force F2 is designed to be greater than or equal to 1.4 times the sum of the gravity G of the rotor system and the maximum value Fn of the axial gas force of the impeller 200 and less than or equal to 1.6 times the sum of the gravity G of the rotor system and the maximum value Fn of the axial gas force of the impeller 200. The fan 1000 of the embodiment of the invention is limited by the parameters, so that the running stability of a rotor system is higher when the fan 1000 works in any direction, and the requirements of miniaturization and light weight of the fan 1000 can be met.

Referring to fig. 5, in one embodiment of the present invention, the first thrust plate 530 and the first end wall 531 are annular. The first grooves 532 are provided on the first end wall 531, and the first grooves 532 are spiral grooves which extend along the circumferential direction of the spindle 500 and extend toward the axis of the spindle 500. The first groove 532 extends in the same direction as the air intake, i.e., from the outer periphery of the first end wall 531 toward the center, and the spiral groove design allows for smoother air flow. The extending directions of the plurality of first grooves 532 are inclined in the opposite direction around the rotation direction of the first thrust plate 530, that is, when the rotation direction of the first thrust plate 530 is clockwise, the extending directions of the plurality of first grooves 532 are inclined around the counterclockwise direction, so that when the spindle 500 drives the first thrust plate 530 to rotate, air flow can more easily enter from the air inlet end of the first grooves 532, and a local high pressure area is formed at the air outlet end of the first grooves 532, thereby increasing the magnitude of the first thrust force formed between the first thrust plate 530 and the sleeve 600.

Referring to fig. 5, it will be appreciated that the end of the first groove 532 remote from the axis is an air inlet end and the end near the axis is an air outlet end. The air inlet end is located the periphery edge department of first end wall 531 for the air can get into first recess 532 along the periphery edge of first end wall 531, thereby is favorable to the air to get into first recess 532, has increased the air input of first recess 532, and then has increased the area that the end formed local high-pressure zone of giving vent to anger, thereby has increased first thrust size, makes rotor system operation more stable, and the stability of fan 1000 is better.

Referring to fig. 5, it can be appreciated that the plurality of first grooves 532 are identical in structure, so that the magnitude and direction of the first thrust force can be more stable. The plurality of first grooves 532 form a first reference circle toward one end of the axis, a diameter D21 defining the first reference circle, a number n of the first grooves 532, and a width B of each first groove 532 on the first reference circle, satisfying: nB/pi D21 is more than or equal to 20% and less than or equal to 65%, so that the stability of the first thrust is improved. It will be appreciated that the ratio of the plurality of first grooves 532 across the first end wall 531 should not be too large or too small. When the duty ratio is too large, the equivalent gap in the first thrust bearing increases and the first thrust force decreases. When the duty ratio is too small, the local high pressure area generated by the plurality of first grooves 532 has limited effect, which is unfavorable for forming stable first thrust, and is unfavorable for improving the stability of the rotor system. More preferably, the first groove 532 parameter may be defined as: the nB/pi D21 is more than or equal to 40% and less than or equal to 60%, so that the stability of the first thrust can be further ensured.

Referring to fig. 5, it can be understood that the first groove 532 includes a first outer line and a first inner line sequentially arranged in the rotation direction of the first thrust plate 530, the tangential angle λ1 of the first outer line at the outer circumferential edge of the first end wall 531 is satisfied by the tangential angle λ1: and the angle of lambda 1 is more than or equal to 45 degrees and less than or equal to 80 degrees, so that air is conveniently and rapidly introduced into the first groove 532, and a local high-pressure area is generated at the air outlet end of the first groove 532, so that stable first thrust is formed. More preferably, the tangential angle λ1 may be defined as: and the lambda 1 is larger than or equal to 70 degrees and smaller than or equal to 75 degrees, so that the air inlet of the first groove 532 is smoother, the air inlet quantity is larger, and the bearing effect of the thrust bearing is better.

Referring to fig. 6, in the first thrust plate 530 according to another embodiment of the present invention, the first end wall 531 is annular, a plurality of first grooves 532 are disposed on the first end wall 531, and the plurality of first grooves 532 are inclined grooves. As shown in fig. 6, it is clear that the width of the air inlet end of the first groove 532 is greater than the width of the air outlet end of the first groove 532, and the first groove 532 may be configured to be gradually narrowed in the air flow direction. It can be appreciated that, on the one hand, the design of the width of the air inlet end is larger, which is favorable for improving the air inflow of the first groove 532, and on the other hand, the air is gradually narrowed after entering from the air inlet end and forms a local high-pressure area at the air outlet end, and because the air is gradually compressed in the first groove 532, a local high-pressure area with larger pressure can be formed at the air outlet end, the first thrust is increased, and the running stability of the rotor system is further improved.

Referring to fig. 7, in the first thrust disk 530 of another embodiment of the present invention, the first end wall 531 is further provided with a first connection groove 533, the first connection groove 533 is a chute, the first connection groove 533 is provided with a plurality of first connection grooves 533, the plurality of first connection grooves 533 are connected to one end of the plurality of first grooves 532 facing the axis, and are disposed at an angle with respect to the corresponding first grooves 532, the angle is greater than 0 degrees and less than 180 degrees, such that the first connection groove 533 is disposed at a bend angle with respect to the first grooves 532, i.e. the first connection groove 533 is connected to the end of the extending direction of the first grooves 532. The first recess 532 is also a tapered slot, thereby forming a hinge slot with the first connection slot 533 on the first end wall 531. It will be appreciated that the air is bent from the air outlet end to the first connection groove 533 after entering from the air inlet end, and the airflow is turned to form a local high-pressure area with a larger area at the connection between the first groove 532 and the first connection groove 533, so that the first thrust is further increased, the rotor system is more stable in operation, and the fan 1000 is better in stability.

Referring to fig. 8, in the first thrust disk 530 of another embodiment of the present invention, the first end wall 531 is further provided with a first connection groove 533, the first connection groove 533 is a spiral groove, the first connection groove 533 is provided with a plurality of first connection grooves 533, the plurality of first connection grooves 533 are connected to one end of the plurality of first grooves 532 facing the axis, and are disposed at an angle with respect to the corresponding first grooves 532, the angle is greater than 0 degrees and less than 180 degrees, such that the first connection groove 533 is disposed at a bending angle with respect to the first grooves 532, i.e. the first connection groove 533 is connected to the end of the extending direction of the first grooves 532. The first groove 532 is also a spiral groove so that a chevron-shaped groove is formed in the first end wall 531 with the first connection groove 533. It will be appreciated that the air is bent from the air outlet end to the first connection groove 533 after entering from the air inlet end, and the airflow is turned to form a local high-pressure area with a larger area at the connection between the first groove 532 and the first connection groove 533, so that the first thrust is further increased, the rotor system is more stable in operation, and the fan 1000 is better in stability.

As other embodiments, there may be various ways of matching the first groove 532 and the first connecting groove 533, for example, the first groove 532 is a spiral groove, the first connecting groove 533 is a chute, and the principle and the effect thereof are substantially the same as those of the above two embodiments, namely, the hinge groove and the chevron groove, which will be understood by reference, and will not be repeated herein.

It is understood that the first groove 532 and the first connection groove 533 may be formed by laser processing, etching processing, or electric discharge machining, which are not particularly limited herein. The first groove 532 and the first connection groove 533 may be integrally formed.

As another embodiment, when the first groove 532 is provided on the end wall of the sleeve 600, the first connection groove 533 is correspondingly provided on the end wall of the sleeve 600.

It will be appreciated that the second thrust plate 540 and the opposite end wall of the sleeve 600 of the present embodiment have a mating feature therebetween, which is substantially the same as the mating feature between the first thrust plate 530 and the opposite end wall of the sleeve 600, and will be understood with reference to the above embodiment, and will not be repeated here.

Referring to fig. 9 and 10, it can be appreciated that the length of the bushing 600 is smaller than the length of the journal 510 by a difference of 8 μm to 16 μm in the axial direction of the main shaft 500. The first thrust plate 530 and the second thrust plate 540 are respectively positioned and installed at both ends of the journal 510, so that the clearance between the two end surfaces of the sleeve 600 and the first thrust plate 530 and the second thrust plate 540 can be conveniently controlled by limiting the parameters between the sleeve 600 and the journal 510, thereby controlling the internal clearance of the two thrust bearings (i.e., the clearance between the first thrust plate 530 and the sleeve 600 and the clearance between the second thrust plate 540 and the sleeve 600) to be 4 μm to 8 μm, and further stabilizing the thrust of the thrust bearings.

Referring to fig. 9 and 10, it can be understood that the inner diameter of the sleeve 600 is larger than the outer diameter of the journal 510 by a difference of 4 to 10 μm, so that the radial bearing can provide a stable radial bearing force when the gap between the inner circumferential wall of the sleeve 600 and the outer circumferential wall of the journal 510 is controlled in the range of 2 to 5 μm, thereby reducing friction between the main shaft 500 and the radial bearing and improving the stability of the rotation of the rotor system.

Referring to fig. 5 and 9, defining an outer diameter D31 of the journal 510, the plurality of first grooves 532 form a first reference circle toward one end of the axis, the diameter D21 of the first reference circle satisfying: d21 And D31. It will be appreciated that by defining the air outlet end of the first recess 532 above the shoulder, a localized high pressure region can be formed in the effective fit gap between the first end wall 531 and the end wall of the sleeve 600, ensuring stable formation of the first thrust force, and avoiding a reduction in the effective area of action between the first recess 532 and the end wall of the sleeve 600, ensuring the magnitude of the first thrust force. Meanwhile, the outer diameter of the sleeve 600 is defined as D41, satisfying: d21 is less than or equal to D41. It will be appreciated that by defining the air outlet end of the first recess 532 within the effective mating gap between the first end wall 531 and the end wall of the sleeve 600, a localized high pressure region can be created within the mating gap, thereby ensuring the magnitude of the first thrust force.

Referring to fig. 9, it can be understood that the outer diameter of the journal 510 is defined as D31, and the outer diameter of the shaft body 520 is defined as D32, satisfying: D32/D31 is more than or equal to 40% and less than or equal to 80%, so that the mass distribution characteristic of the rotor system is more uniform. Too small of the above-mentioned ratio parameters may result in a reduction of the effective active area of the radial bearing, which may not be able to achieve sufficient radial bearing capacity to support the rotor system; too large a ratio parameter may result in too large an outer diameter of the journal 510, and the size of the entire blower 1000 may be increased, failing to meet the miniaturization requirement. More preferably, the D32/D31 is limited to be less than or equal to 45% and less than or equal to 55%, so that the mass distribution of the rotor system is better, and the sufficient radial bearing capacity can be provided while the miniaturization of the fan 1000 is satisfied. In addition, the outer diameter D32 of the limiting shaft body 520 is more than or equal to 4mm, so that the strength of the main shaft 500 is ensured, and the main shaft 500 is prevented from breaking in the high-speed rotation process.

Referring to fig. 9, it can be understood that the length of the journal 510 is L0 and the length of the main shaft 500 is L along the axial direction of the main shaft 500, satisfying: l0 is more than or equal to 0.2L and less than or equal to 0.8L, so that the effective acting area of the journal 510 and the shaft sleeve 600 is ensured, and the bearing capacity of the radial bearing meets the requirement. More preferably, 0.4 L.ltoreq.L0.ltoreq.0.5L is defined.

Referring to fig. 9, it will be appreciated that a plurality of third grooves 511 are provided on the outer circumferential wall of the journal 510 and extend spirally in the axial direction of the spindle 500 to form a plurality of spiral grooves, the air inlet ends of which are located at one end wall of the journal 510 and the air outlet ends of which are located between the two end walls of the journal 510. The plurality of third grooves 511 may be uniformly distributed along the circumferential direction of the journal 510. The outer circumferential wall of the journal 510 is further provided with a third connection groove 512, and the third connection groove 512 is connected to one end of the third groove 511 far from the end wall of the journal 510 and is disposed at an angle to the third groove 511, the angle being greater than 0 degrees and less than 180 degrees, so that the third connection groove 512 is disposed to be bent with respect to the third groove 511, that is, the third connection groove 512 is connected to the end of the third groove 511 in the extending direction. The first connection groove 533 is also a spiral groove so that a chevron groove is formed on the outer circumferential wall of the journal 510 with the third connection groove 512. It can be appreciated that the air is bent from the air outlet end to the third connecting groove 512 after entering from the air inlet end, and the airflow is turned to form a local high-pressure area with larger area at the connection position of the third groove 511 and the third connecting groove 512, so that the radial bearing capacity is further increased, the running of the rotor system is more stable, and the stability of the fan 1000 is better.

Referring to fig. 9, it can be appreciated that one end of the third groove 511 is located at one of the end walls of the journal 510. The third groove 511 is located at one end of the end wall of the journal 510 and is an air inlet end, so that air can enter the third groove 511 from the periphery of the end wall of the journal 510, air can enter the third groove 511, the air inflow of the third groove 511 is increased, the area of a local high-pressure area formed by the air outlet end is increased, the radial bearing capacity is increased, the rotor system is enabled to run more stably, and the stability of the fan 1000 is better.

Referring to fig. 9, in the rotor system according to an embodiment of the present invention, one of the outer circumferential wall of the journal 510 and the inner circumferential wall of the sleeve 600 is provided with a plurality of groove groups 513, and the plurality of groove groups 513 are disposed at intervals in the axial direction of the journal 510, and each groove group 513 includes a plurality of third grooves 511 uniformly distributed in the circumferential direction of the journal 510. It will be appreciated that the plurality of groove sets 513 correspond to a plurality of radial bearings, thereby providing a greater and more stable radial bearing capacity, thereby enabling the rotor system to float relative to the radial bearings, reducing frictional losses between the journal 510 and the sleeve 600, and thus enabling the rotor system to achieve higher rotational speeds.

Referring to fig. 9, it can be understood that the total length of the plurality of groove groups 513 is L1 along the axial direction of the spindle 500, and the total length L1 of the plurality of groove groups 513 is equal to the sum of the length L11 of the first groove group and the length L12 of the second groove group in the embodiment shown in fig. 9, and the length of the journal 510 is L0, so that: L1/L0 is more than or equal to 50% and less than or equal to 98%, so that the rotor system can receive enough radial bearing force, the running stability of the rotor system is ensured, the deflection amplitude of the rotor system is reduced, the rotor system can obtain higher rotating speed, and the influence of the fan 1000 on the running of the rotor system in any direction is greatly reduced. More preferably, the limit of L1/L0 is more than or equal to 80% and less than or equal to 98%, so that the radial bearing force born by the rotor system is larger, the rotation of the rotor system is more stable, and the operation of the fan 1000 is more stable.

Referring to fig. 11, in another embodiment of the fan 1000 of the present invention, an end wall of the sleeve 600 opposite to the first end wall 531 is conical, and the first end wall 531 engaged with the sleeve is also conical. Correspondingly, the end wall of the sleeve 600 opposite to the second end wall 541 is conical, and the second end wall 541 cooperating therewith is conical. It will be appreciated that, during high speed operation of the rotor system, the thrust direction formed by the two thrust bearings formed between the sleeve 600 and the first thrust plate 530 and the second thrust plate 540 is perpendicular to the conical surface of the sleeve 600, so that the thrust bearing can be decomposed into a radial bearing force and an axial bearing force, and radial support and thrust are realized, so that the operation of the rotor system is more stable.

Referring to fig. 12, in another embodiment of the fan 1000 of the present invention, an end wall of the sleeve 600 opposite to the first end wall 531 is spherical, and the first end wall 531 engaged with the sleeve is also spherical. Correspondingly, the end wall of the sleeve 600 opposite to the second end wall 541 is also spherical, and the second end wall 541 cooperating therewith is also spherical. It can be appreciated that, when the rotor system operates at a high speed, the thrust direction formed by the two thrust bearings formed between the sleeve 600 and the first thrust disk 530 and the second thrust disk 540 is the normal direction of the spherical surface of the sleeve 600, so that the thrust bearing can be decomposed into a radial bearing force and an axial bearing force, and radial support and thrust are realized, so that the operation of the rotor system is more stable.

Referring to fig. 1, a cleaning apparatus according to an embodiment of the present invention may be a hand-held cleaner, a bucket cleaner, or a sweeping robot, or may be other cleaning apparatus. The cleaning device according to the embodiment of the present invention includes the blower 1000 according to the above embodiment, the supporting frame 410 is fixed to the casing 400 by setting the shaft sleeve 600, and the rotor system including the impeller 200, the spindle 500, the first thrust disk 530, the second thrust disk 540 and the rotor 800, where the spindle 500 is rotatably disposed in the radial bearing formed by the shaft sleeve 600, and the radial bearing provides a radial bearing force for the rotor system to enable the spindle 500 to be separated from the shaft sleeve 600 when the spindle 500 rotates at a high speed, so that the friction between the spindle 500 and the shaft sleeve 600 is reduced; the first thrust disc 530 and the second thrust disc 540 are fixed on the main shaft 500 and form two thrust bearings with opposite acting force directions with the shaft sleeve 600 respectively, under the maximum rotation speed of the fan 1000, the thrust forces of the two thrust bearings are designed to be the sum of the gravity of the rotor system and the maximum value of the axial gas force of the impeller 200, which is 1.2-2 times, so that the shaft sleeve 600 can be separated from the first thrust disc 530 and the second thrust disc 540, the stability of the rotor system in the axial direction is improved, the influence of the fan 1000 on the operation of the rotor system when working in any direction is reduced, the deflection of the rotor system is effectively reduced, the rotor system can stably operate under the highest rotation speed under various using conditions, and the requirements of miniaturization and light weight of the fan 1000 are simultaneously ensured; by adopting the gas bearing to reduce the friction of the rotor system, the running of the rotor system can be more stable, the performance and mechanical noise of the fan 1000 are improved, and the stability and the highest rotating speed of the fan 1000 are improved.

Since the cleaning device adopts all the technical solutions of the blower 1000 in the foregoing embodiments, at least all the beneficial effects brought by the technical solutions in the foregoing embodiments are not described herein.

The embodiments of the present invention have been described in detail with reference to the accompanying drawings, but the present invention is not limited to the above embodiments, and various changes can be made within the knowledge of one of ordinary skill in the art without departing from the spirit of the present invention.

Claims

1. The fan, its characterized in that includes:

a shell provided with a supporting frame;

the shaft sleeve is fixed on the supporting frame;

the rotor system comprises an impeller, a main shaft, a first thrust disc, a second thrust disc and a rotor, wherein the main shaft is rotationally arranged in the shaft sleeve, part of the outer peripheral wall of the main shaft is in clearance fit with the inner peripheral wall of the shaft sleeve, the impeller is fixed at one end of the main shaft, the rotor is fixed at the other end of the main shaft, the first thrust disc is fixed at the main shaft and in clearance fit with the shaft sleeve, one end of the first thrust disc, which faces the shaft sleeve, is provided with a first end wall, the opposite end wall of the first end wall or the shaft sleeve is provided with a plurality of first grooves, the first grooves are arranged at intervals along the circumferential direction of the main shaft, the second thrust disc is fixed at the main shaft and in clearance fit with the shaft sleeve, one end of the second thrust disc, which faces the shaft sleeve, is provided with a plurality of second grooves, and the opposite end wall of the second end wall or the shaft sleeve is provided with a plurality of second grooves are arranged at intervals along the circumferential direction of the main shaft;

A stator which is arranged around the periphery of the rotor;

the gravity of the rotor system is G, the diameter of an air suction port of the impeller is D11, and the maximum outer diameter of the impeller is D12; the maximum vacuum degree of the fan is P, under the maximum rotating speed of the fan, the thrust of the first thrust disc is F1, and the thrust of the second thrust disc is F2, so that the requirements are satisfied: F1/(G+P (pi D12) of 1.2 ² /4-πD11 ² (4))is less than or equal to 2, and F2/(G+P (pi D12) is less than or equal to 1.2 ² /4-πD11 ² /4））≤2。

2. The blower of claim 1, wherein: the first grooves are formed in the first end wall, extend towards the axis of the main shaft and incline in the direction opposite to the rotation direction around the first thrust disc.

3. The blower of claim 2, wherein: an end of the first groove remote from the axis is located at the peripheral edge of the first end wall.

4. The blower of claim 2, wherein: the plurality of first grooves are identical in structure and face one end of the axis to form a first reference circle, the diameter of the first reference circle is D21, the number of the first grooves is n, the width of the first grooves on the first reference circle is B, and the requirements are met: nB/pi D21 is more than or equal to 20% and less than or equal to 65%.

5. The blower of claim 2, wherein: the first groove comprises a first outer molded line and a first inner molded line which are sequentially arranged along the rotation direction of the first thrust disk, the tangential angle of the first outer molded line at the peripheral edge of the first end wall is lambda 1, and the requirements are met: lambda 1 is more than or equal to 45 degrees and less than or equal to 80 degrees.

6. The blower of claim 2, wherein: the first end wall or the opposite end wall of the shaft sleeve is provided with a plurality of first connecting grooves, the first connecting grooves are respectively correspondingly connected to one ends of the first grooves facing the axis, and the first grooves are bent and arranged relative to the first grooves.

7. The blower of claim 1, wherein: the main shaft comprises a shaft neck and a shaft body, the diameter of the shaft neck is larger than that of the shaft body, the first thrust disc is sleeved on the shaft body and is abutted to one end, facing the impeller, of the shaft neck, and the second thrust disc is sleeved on the shaft body and is abutted to one end, far away from the impeller, of the shaft neck.

8. The blower of claim 7, wherein: the length of the shaft sleeve is smaller than the length of the shaft journal and the difference is 8-16 μm.

9. The blower of claim 7, wherein: the external diameter of axle journal is D31, and a plurality of first recesses are towards the one end of the axis of main shaft forms first reference circle, the diameter of first reference circle is D21, the external diameter of axle sleeve is D41, satisfies: d21 Not less than D31 and D21 not more than D41.

10. The blower of claim 7, wherein: the external diameter of axle journal is D31, the external diameter of axle body is D32, satisfies: D32/D31 is more than or equal to 40% and less than or equal to 80%, and D32 is more than or equal to 4mm.

11. The blower of claim 7, wherein: the second thrust disk is annular, the external diameter of the second thrust disk is D22, the internal diameter of the stator is D51, the external diameter of the shaft neck is D31, and the requirements are satisfied: 1.3D31D 22 is less than or equal to 0.98D51.

12. The blower of claim 7, wherein: the length of the shaft neck is L0, and the length of the main shaft is L, so that the following conditions are satisfied: l0 is more than or equal to 0.2L and less than or equal to 0.8L.

13. The blower of claim 7, wherein: the outer peripheral wall of the shaft neck is in clearance fit with the inner peripheral wall of the shaft sleeve, one of the outer peripheral wall of the shaft neck and the inner peripheral wall of the shaft sleeve is provided with a plurality of third grooves, and the third grooves are arranged at intervals along the circumferential direction of the main shaft.

14. The blower of claim 13, wherein: the plurality of third grooves are formed in the outer peripheral wall of the shaft neck and extend along the axial direction of the main shaft in a spiral mode, third connecting grooves are further formed in the outer peripheral wall of the shaft neck and connected to one end, far away from the end wall of the shaft neck, of the third grooves, and the third grooves are bent relative to the third grooves.

15. The blower of claim 1, wherein: the first end wall is annular, conical or spherical.

16. Cleaning device, its characterized in that: comprising a wind turbine according to any one of claims 1 to 15.