CN217233852U - Fan and cleaning device - Google Patents

Abstract

The utility model discloses a fan and cleaning equipment, wherein the fan comprises a main shaft, an impeller, a motor and a casing, and the impeller is connected with the main shaft; the main shaft is supported through a bearing assembly, the bearing assembly comprises a thrust assembly and a shaft sleeve sleeved on the main shaft, the shaft sleeve comprises at least two shaft sleeve units, and the shaft sleeve units are assembled along the circumferential direction of the main shaft to form the shaft sleeve. The bearing assembly is adopted to replace the traditional ball bearing, so that the friction between the main shaft and the shaft sleeve can be reduced, and the service life of the bearing assembly is prolonged. After the dynamic balance is manufactured, the shaft sleeve unit is assembled along the outer wall of the main shaft to complete the assembly of the shaft sleeve, the thrust assembly does not need to be disassembled and then sleeved into the shaft sleeve from one side of the main shaft, the influence of the assembly process of the shaft sleeve on the residual unbalance of the rotor system is effectively reduced, the problem of the dynamic balance of the rotor system is solved, and the operation stability of the fan is improved.

Description

Fan and cleaning device

Technical Field

The utility model belongs to the technical field of the relevant technique of electrical apparatus and specifically relates to a fan and cleaning device are related to.

Background

The fan of the dust collector works by the rotation of the impeller, and negative pressure is generated at the inlet of the fan, so that suction force is generated on dust and the like. The pivot of traditional fan generally adopts ball bearing to support, can produce mechanical friction during ball bearing operation, and especially the rotational speed of impeller risees back mechanical friction more obvious, reduces ball bearing's life.

In the related art, a gas bearing is used instead of a ball bearing, and the friction between the rotating shaft and the bearing can be reduced by supporting the rotating shaft through a radial bearing and an axial thrust piece. When dynamic balance is carried out, the radial bearing can generate play to influence correction, the radial bearing needs to be dismounted, and other parts such as the impeller, the rotating shaft and the thrust piece are assembled and then are subjected to dynamic balance manufacturing; after the dynamic balance is completed, the radial bearing is reinstalled after the components such as the thrust piece and the like are disassembled, but the residual unbalance of the rotor system is increased easily in the process of reinstallation after disassembly, so that the vibration is large, and the running stability of the fan is reduced.

SUMMERY OF THE UTILITY MODEL

The utility model discloses aim at solving one of the technical problem that exists among the prior art at least. Therefore, the utility model provides a fan adopts the axle sleeve installation of components of a whole that can function independently structure more nimble, effectively reduces the influence of axle sleeve assembling process to dynamic balance, improves fan moving stability.

The utility model discloses still provide the cleaning device including above-mentioned fan.

According to the utility model discloses a fan of first aspect embodiment, include:

a housing;

the main shaft is rotatably arranged in the shell;

an impeller connected with the main shaft;

the bearing assembly comprises a thrust assembly and a shaft sleeve sleeved on the spindle, the thrust assembly is arranged at the end part of the shaft sleeve along the axial direction of the spindle and is connected with the spindle, the shaft sleeve is fixedly connected with the casing, the shaft sleeve is in clearance fit with the spindle along the radial direction of the spindle, and the shaft sleeve is in clearance fit with the thrust assembly along the axial direction of the spindle;

the shaft sleeve comprises at least two shaft sleeve units, and the shaft sleeve units are assembled along the circumferential direction of the main shaft to form the shaft sleeve.

According to the utility model discloses fan has following beneficial effect at least:

the fan drives the impeller to rotate at high speed through the main shaft, the bearing assembly replaces a traditional ball bearing, the shaft sleeve and the thrust assembly are matched to form a gas bearing, radial bearing capacity and axial bearing capacity can be provided for the main shaft, the main shaft can be separated from the shaft sleeve when the main shaft runs at high speed, friction between the main shaft and the shaft sleeve is reduced, and the service life of the bearing assembly is prolonged; and the axle sleeve accessible two at least axle sleeve units are assembled and are formed, the axle sleeve adopts split type structure promptly, when doing dynamic balance like this, carry out the dynamic balance preparation with main shaft and thrust subassembly together, after the dynamic balance preparation is accomplished, only need assemble the assembly that can accomplish the axle sleeve with the axle sleeve unit along the outer wall of main shaft, need not to embolia the axle sleeve from one side of main shaft after dismantling the thrust subassembly, effectively reduce the influence of axle sleeve assembling process to the remaining unbalance amount of rotor system, solve the problem of rotor system dynamic balance, improve fan operating stability.

According to some embodiments of the utility model, the casing is equipped with the support frame, the support frame cover is located the outside of axle sleeve, every the axle sleeve unit all with the inside wall fixed connection of support frame.

According to some embodiments of the utility model, the fan still includes diffuser and fan housing, the diffuser connect in the support frame, the fan housing with the casing is connected just the impeller with form inlet air duct between the fan housing, the diffuser with form between the fan housing with the diffusion passageway of inlet air duct intercommunication.

According to some embodiments of the utility model, the thrust subassembly includes first thrust dish and second thrust dish, first thrust dish with second thrust dish is located respectively the both ends of axle sleeve, first thrust dish with second thrust dish all with main shaft fixed connection.

According to some embodiments of the utility model, the main shaft includes axle body and axle journal, the diameter of axle journal is greater than the diameter of axle body, the axle sleeve is located the axle journal, first thrust dish with second thrust dish all with the axle body is connected.

According to some embodiments of the present invention, the axle journal with the clearance between the axle sleeve is f, satisfies: f is (d-b)/2, and 0.002mm ≦ (d-b)/2 ≦ 0.01mm, wherein d is the inner diameter of the bushing and b is the diameter of the journal.

According to some embodiments of the utility model, the lateral wall of axle journal or the inside wall of axle sleeve is equipped with many first recesses, many first recess is followed the circumference interval of main shaft sets up.

According to some embodiments of the utility model, first thrust dish with be equipped with many second recesses between the axle sleeve, many the second recess is followed the circumference interval distribution of main shaft in the terminal surface of first thrust dish or the terminal surface of axle sleeve, second thrust dish with be equipped with many third recesses between the axle sleeve, many the third recess is followed the circumference interval distribution of main shaft in the terminal surface of second thrust dish or the terminal surface of axle sleeve.

According to the utility model discloses a some embodiments, first recess the degree of depth of second recess and third recess is h, satisfies: h is less than or equal to 0.005 mm.

According to the utility model discloses a some embodiments work as the second recess is located the terminal surface of first thrust dish, second recess position is followed the radial minimum diameter of main shaft is g1, satisfies: g1 > d; or when the third groove is arranged on the end face of the second thrust disk, the minimum diameter of the position of the third groove along the radial direction of the main shaft is g2, which satisfies the following conditions: g2 > d, and the inner diameter of the shaft sleeve is d.

According to some embodiments of the utility model, the fan still includes the stator and is located rotor in the stator, the rotor with the main shaft is connected, the periphery wall of main shaft is equipped with the ring channel that is used for filling glue, the ring channel is located the main shaft with the junction of rotor.

According to the utility model discloses a cleaning device of second aspect embodiment, including the fan of above-mentioned first aspect embodiment.

Since the cleaning device adopts all the technical solutions of the fan of the above embodiments, at least all the advantages brought by the technical solutions of the above embodiments are achieved.

Additional features and advantages of the invention will be set forth in the description which follows, and in part will be obvious from the description, or may be learned by the practice of the invention.

Drawings

Fig. 1 is an exploded schematic view of a fan according to an embodiment of the present invention;

fig. 2 is a schematic cross-sectional view of a fan according to an embodiment of the present invention;

fig. 3 is a schematic cross-sectional view of a rotor system according to an embodiment of the present invention;

FIG. 4 is an exploded view of a transfer system according to the related art;

fig. 5 is an exploded schematic view of a rotor system according to an embodiment of the present invention;

fig. 6 is a schematic view of a connection structure of the spindle and the thrust assembly according to an embodiment of the present invention;

fig. 7 is a front view of a spindle and thrust assembly connection structure according to an embodiment of the present invention;

fig. 8 is a schematic front view of a first thrust plate according to an embodiment of the present invention.

Reference numerals:

a fan housing 100; an air inlet 110;

an impeller 200; an air intake passage 210;

a diffuser 300; a diffuser passage 310;

a housing 400; a support frame 410;

a motor 500; a magnetic ring 510; a stator 520;

a bearing assembly 600; a shaft sleeve 610; a bushing unit 611; a first thrust disk 620; a second recess 621; a second thrust disk 630;

a main shaft 700; a shaft body 710; an annular groove 711; a journal 720; a first groove 721;

a rotor system 800.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are exemplary only for the purpose of explaining the present invention, and should not be construed as limiting the present invention.

In the description of the present invention, it should be understood that the terms up, down, etc. indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, which are only for convenience of description of the present invention and simplification of description, and do not indicate or imply that the device 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, if there are first and second descriptions for distinguishing technical features, they are not interpreted as indicating or implying relative importance or implicitly indicating the number of indicated technical features or implicitly indicating the precedence of the indicated technical features.

In the description of the present invention, it should be noted that words such as setting, installing, connecting, etc. should be understood in a broad sense, and those skilled in the art can reasonably determine the specific meaning of the words in the present invention by combining the specific contents of the technical solution.

In the description of the present invention, the description of some embodiments, specific embodiments, etc. means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present invention. Throughout this specification, the schematic representations of the terms used above do not necessarily refer to the same implementation or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

The technical solutions of the present invention will be described clearly and completely with reference to the accompanying drawings, and obviously, the embodiments described below are some, not all embodiments of the present invention.

The fan according to the embodiment of the present invention is described with reference to fig. 1 to 8, and is applied to a cleaning device such as a vacuum cleaner.

Referring to fig. 1 and 2, a fan according to an embodiment includes a fan housing 100, a casing 400, an impeller 200, a diffuser 300, and a motor 500, wherein a rotatable spindle 700 is installed in the casing 400, one end of the spindle 700 is connected to the motor 500, the other end of the spindle 700 is connected to the impeller 200, the motor 500 drives the spindle 700 to rotate, and the spindle 700 can drive the impeller 200 to rotate at a high speed. The upper end of the casing 400 is provided with the fan housing 100 and the diffuser 300, the impeller 200 and the diffuser 300 are both located inside the fan housing 100, wherein the fan housing 100 is provided with an air inlet 110, an air inlet passage 210 is formed between the impeller 200 and the fan housing 100, the diffuser 300 is fixedly connected with the casing 400, a diffuser passage 310 communicated with the air inlet passage 210 is formed between the diffuser 300 and the fan housing 100, the motor 500 drives the impeller 200 to rotate to generate air flow, the air flow enters the air inlet passage 210 from the air inlet 110 and is diffused through the diffuser passage 310, so that the pressure of the air flow is increased, and the suction force generated by the fan is increased. Taking a dust collector as an example, under the action of negative pressure generated by a fan, foreign matters such as dust and garbage can be sucked into a filter cloth bag or other processing structures of the dust collector to finish dust collection and other work.

Fig. 2 is a schematic cross-sectional view of a blower according to an embodiment of the present invention, a bearing assembly 600 for supporting a spindle 700 is further disposed in the casing 400, the bearing assembly 600 includes a shaft sleeve 610 and a thrust assembly, wherein the shaft sleeve 610 is sleeved on the spindle 700, a clearance fit is provided between the shaft sleeve 610 and the spindle 700, the shaft sleeve 610 is fixed in the casing 400, and the shaft sleeve 610 can be understood as a radial bearing of the spindle 700. The thrust assembly is arranged at the end of the shaft sleeve 610, the thrust assembly supports the spindle 700 in the axial direction of the spindle 700, the thrust assembly is fixedly connected with the spindle 700, the thrust assembly is in clearance fit with the shaft sleeve 610, and the thrust assembly can be understood as a thrust bearing of the spindle 700. Specifically, there is a gap between the sleeve 610 and the spindle 700 and between the sleeve 610 and the thrust assembly, and it is understood that the sleeve 610 and the thrust assembly cooperate to form a gas bearing, also called an air bearing, and the spindle 700 can support the spindle 700 in the radial and axial directions during high-speed rotation, so that the spindle 700 can stably operate, and thus the gas bearing is used to replace the conventional ball bearing.

Referring to fig. 2, the motor 500 includes a stator 520 and a rotor disposed in the stator 520, the rotor includes a magnetic ring 510 and is connected to a spindle 700, the upper end of the spindle 700 is connected to the impeller 200, the lower end of the spindle is connected to the magnetic ring 510 of the motor 500, a bearing assembly 600 is mounted in the middle of the spindle 700, the axial height of a sleeve 610 is less than the axial height of the spindle 700, the sleeve 610 is sleeved on the outer sidewall of the spindle 700, and a thrust assembly includes thrust structures disposed at the upper and lower ends of the sleeve 610, which may be discs, disks or other thrust members.

It will be appreciated that since the thrust assembly is fixedly connected to the spindle 700 and the sleeve 610 is fixedly connected to the housing 400, the thrust assembly can rotate with the spindle 700 and the sleeve 610 is stationary. When the spindle 700 rotates at a high speed, an air film is formed after air pressure is stabilized in a gap between the sleeve 610 and the spindle 700 and a gap between the sleeve 610 and the thrust structure, so that a dynamic pressure effect is generated, and thus, bearing force can be provided to the spindle 700 in both axial and radial directions to support the spindle 700 to rotate at a high speed, so that the spindle 700 can float and be separated from the sleeve 610.

Compared with a ball bearing, the gas bearing can effectively reduce the friction between the main shaft 700 and the shaft sleeve 610, is beneficial to prolonging the service life of the bearing assembly 600, can keep lower vibration level at the same time, and achieves the purpose of improving the performance and mechanical noise of the fan, and the gas bearing can provide higher radial and axial bearing capacity, has higher rotation precision, reduces the power loss to the minimum while running at high rotation speed, can reach more than 100000 r/min, and meets the high suction requirement of cleaning equipment such as a dust collector.

Referring to fig. 3, in the embodiment, the impeller 200, the main shaft 700, the bearing assembly 600 and the rotor are combined into a rotor system 800, wherein the rotor is a magnetic ring 510 sleeved on the main shaft 700, and fig. 3 is a schematic cross-sectional structure diagram of the rotor system 800. In view of the high speed rotation in a wind turbine, dynamic balancing is required to ensure that the rotor system 800 operates stably at high speeds. Since the spindle 700 and the sleeve 610 have a certain gap therebetween in the embodiment, if the sleeve 610 and the spindle 700 are balanced together, the sleeve 610 moves up and down, and thus cannot operate stably.

In the related art, the shaft sleeve 610 needs to be detached, the spindle 700, the thrust assembly, the magnetic ring 510 and the like are assembled together to perform dynamic balance manufacturing, after the dynamic balance is completed, the thrust structure and the magnetic ring 510 on one side need to be detached, and then the shaft sleeve 610 needs to be remounted to form the whole rotor system 800, however, the thrust structure and the magnetic ring 510 are prone to deviation in the process of being detached and then being mounted, and the residual unbalance of the whole rotor system 800 is prone to increase. It should be noted that the residual unbalance amount is the unbalance amount remaining on the rotor system 800 after balancing, and the residual unbalance amount has a corresponding allowable value range, and if the thrust assembly and the magnetic ring 510 are disassembled and reassembled after the dynamic balancing is completed, for example, an assembly error may increase the residual unbalance amount, affect the dynamic balancing correction effect, thereby causing a large vibration and reducing the stability of the rotor system 800 in high-speed operation. Fig. 4 is an exploded view of a rotor system according to the related art, in which a sleeve 610 is integrally formed, and the sleeve 610 is assembled to the main shaft 700 only from one side of the main shaft 700, which results in low flexibility in installation.

Referring to fig. 5, fig. 5 is an exploded schematic view of a rotor system 800 according to an embodiment of the present invention. It can be understood that, in the embodiment, the shaft sleeve 610 adopts a split structure, the shaft sleeve 610 is an annular cylinder as a whole, the shaft sleeve 610 is formed by assembling two shaft sleeve units 611, and the cross section of each shaft sleeve unit 611 is in a semi-annular shape, so that the two shaft sleeve units 611 can be assembled along the circumferential direction of the main shaft 700 to form the whole shaft sleeve 610 during assembly, the shaft sleeve 610 is disassembled into two symmetrical shaft sleeve units 611 along the circumferential direction, and meanwhile, each shaft sleeve unit 611 is fixedly connected with the housing 400, so that the assembled shaft sleeve 610 can maintain stability as a whole, and each shaft sleeve unit 611 is in clearance fit with the main shaft 700.

It can be understood that, when the rotor system 800 of the above embodiment is dynamically balanced, the spindle 700, the thrust assembly and the magnetic ring 510 are dynamically balanced, after the dynamic balance is completed, the two shaft sleeve units 611 are assembled along the outer wall of the spindle 700 to complete the assembly of the shaft sleeve 610, and the shaft sleeve 610 is sleeved from one side of the spindle 700 without disassembling the thrust assembly, that is, the thrust assembly and the magnetic ring 510 are not required to be disassembled after the dynamic balance is completed, so that the influence of the assembly process of the shaft sleeve 610 on the residual unbalance of the rotor system 800 is effectively reduced, the problem of the dynamic balance of the rotor system 800 is solved, and the vibration of the rotor system 800 is reduced, and the operation stability of the fan is improved.

It should be noted that, in the embodiment, the shaft sleeve 610 is not limited to be split into two shaft sleeve units 611, and the shaft sleeve 610 may also be formed by assembling a plurality of shaft sleeve units 611, for example, the shaft sleeve 610 may be split into three shaft sleeve units 611 symmetrically distributed, and the three shaft sleeve units 611 may be assembled into an annular shaft sleeve 610 along the circumferential direction; four or more shaft sleeve units 611 can be assembled to form the shaft sleeve 610, and the details are not further limited.

Referring to fig. 1 and 2, in some embodiments, a support frame 410 is disposed in a casing 400 along an axial direction of a main shaft 700, the support frame 410 is substantially of a sleeve structure, the support frame 410 is located in a middle position of the casing 400, a through hole in a center of the support frame 410 is a mounting hole, and a rotor system 800 is mounted at the position of the support frame 410, wherein the support frame 410 is sleeved outside a shaft sleeve 610, so that the shaft sleeve 610 is fixed in the mounting hole, and an outer side wall of the shaft sleeve 610 can be connected with an inner side wall of the mounting hole by glue. Specifically, after the dynamic balance is manufactured, the shaft sleeve units 611 are surrounded on the outer side of the main shaft 700, adjacent shaft sleeve units 611 can be fixed through glue, the shaft sleeve units 611 are connected to form the integral shaft sleeve 610, and then the entire rotor system 800 is assembled on the support frame 410. In the embodiment, the outer sidewall of each bushing unit 611 is connected to the inner sidewall of the mounting hole by glue, so that the bushing 610 is fixed in the support bracket 410, and the gap between the bushing 610 and the main shaft 700 is maintained stable. Of course, the shaft sleeve 610 may also be connected to the supporting frame 410 by fastening means such as clamping, interference fit, etc., and is not limited in detail herein.

It should be noted that, as shown in fig. 2, in an embodiment, the diffuser 300 may be connected to an outer side of the support frame 410, and the diffuser 300 is disposed at an end of the support frame 410 close to the impeller 200. The casing 400 may further fix the diffuser 300 by a snap structure (not shown) so that the diffuser 300 can be stably mounted on the casing 400. In addition, the supporting frame 410 and the casing 400 are integrally formed, so that the overall assembly strength of the rotor system 800 and the casing 400 can be improved, and the structure is more reliable.

Referring to fig. 1, the diffuser 300 includes a mounting hub and blades distributed along a circumferential direction of the mounting hub, wherein the mounting hub is fixedly connected to a support frame 410, and a diffuser passage 310 is defined between the mounting hub, the blades and the wind shield 100, and the diffuser passage 310 may be understood as a primary diffuser passage. In some embodiments, a diffuser structure may be further added in the casing 400, and a secondary diffuser channel communicated with the primary diffuser channel may be defined by the diffuser structure, so that the airflow can be sequentially diffused through the primary diffuser channel and the secondary diffuser channel after passing through the air inlet channel 210, and the pressure of the airflow is further raised to improve the suction force.

Referring to fig. 5, in some embodiments, the thrust assembly includes a first thrust disk 620 and a second thrust disk 630, the first thrust disk 620 and the second thrust disk 630 are each in a disk shape and fixed to the main shaft 700, and the first thrust disk 620 and the second thrust disk 630 are respectively located at both ends of the sleeve 610 in the axial direction. It can be appreciated that where the first thrust disk 620 is located at the end of the main shaft 700 near the impeller 200, the first thrust disk 620 is in clearance fit with the sleeve 610; a second thrust disk 630 is located at one end of the main shaft 700 near the motor 500, and the second thrust disk 630 is in clearance fit with the sleeve 610.

It should be noted that, as shown in fig. 5, the main shaft 700 includes a shaft body 710 and a journal 720, the journal 720 is located at a middle position of the shaft body 710, and the diameter of the journal 720 is larger than that of the shaft body 710. The shaft sleeve 610 is sleeved on the shaft neck 720, and the impeller 200 and the magnetic ring 510 are respectively connected to the shaft bodies 710 at two ends of the main shaft 700. It can be understood that the first thrust disk 620 and the second thrust disk 630 are connected to abut against the end face of the shaft neck 720 along the axial direction, the length of the shaft sleeve 610 may be slightly smaller than the length of the shaft neck 720, and the shaft neck 720 axially positions the first thrust disk 620 and the second thrust disk 630 so that the first thrust disk 620 and the second thrust disk 630 can be separated from the shaft sleeve 610 by a certain gap.

Referring to fig. 6 and 7, it can be understood that the main shaft 700 is connected with the first thrust disk 620 and the second thrust disk 630 to form an integral structure, after the dynamic balance of the rotor system 800 is completed, the sleeve unit 611 can be directly assembled on the journal 720 to form the sleeve 610, so that a gap is formed between the sleeve 610 and the journal 720, the assembly process does not need to disassemble the first thrust disk 620 and the second thrust disk 630, the integral structure is favorable for reducing the assembly error of the thrust assembly, and the main shaft 700 and the bearing assembly 600 have high coaxiality, so that high radial and axial rotation accuracy can be provided for the main shaft 700 through the gas bearing. It should be noted that the first thrust disk 620 and the second thrust disk 630 may be connected to the main shaft 700 by glue, or may be connected by interference fit, welding, or the like, and is not limited herein.

Referring to fig. 3, it can be understood that the gap between the main shaft 700 and the sleeve 610 is a radial gap, which is required to satisfy that when the main shaft 700 rotates at a high speed, the air pressure between the main shaft 700 and the sleeve 610 can form a stable air film, and the main shaft 700 is supported by the air film through a dynamic pressure effect, it should be noted that the air film thickness forms a wedge shape in the circumferential direction, a high pressure region is generated at a position where the air film thickness is small, and a radial bearing force is provided for the main shaft 700 through the high pressure region, which may affect the stability of the air film in the case that the gap between the main shaft 700 and the sleeve 610 is too small or too large.

In an embodiment, as shown in fig. 3, the inner diameter of the shaft sleeve 610 is d, the diameter of the shaft neck 720 is b, and the gap between the shaft neck 720 and the shaft sleeve 610 is f ═ d-b)/2, which satisfies 0.002mm ≦ d-b)/2 ≦ 0.01mm, that is, the radial gap between the shaft neck 720 and the shaft sleeve 610 ranges from 0.002mm (mm) to 0.01mm (mm), for example, the radial gap may be 0.002mm, 0.004mm, 0.01mm, etc.; as another specific example, where the inner diameter of the bushing 610 is 8.120mm and the diameter of the journal 720 is 8.110mm, a radial clearance of 0.005mm may be achieved. It should be noted that the gap between the shaft sleeve 610 and the first thrust disk 620 and the second thrust disk 630 is an axial gap, and the value range of the axial gap may be the same as or different from the value range of the radial gap. In some preferred embodiments, the radial clearance is between 0.002mm and 0.006mm and the axial clearance is about 0.004 mm.

Referring to fig. 6 and 7, in some embodiments, the outer sidewall of the journal 720 is provided with a plurality of first grooves 721, and the plurality of first grooves 721 are circumferentially spaced. The end surface of the first thrust disk 620 facing the shaft sleeve 610 is provided with a plurality of second grooves 621, the end surface of the second thrust disk 630 facing the shaft sleeve 610 is provided with a plurality of third grooves (not shown in the drawings), and the plurality of second grooves 621 and the plurality of third grooves are all circumferentially spaced apart. It can be understood that air can enter the axial gaps at both ends of the shaft sleeve 610 along the second groove 621 and the third groove and enter the radial gaps from the axial gaps, so that high pressure regions can be formed in the axial gaps and the radial gaps respectively, and a stable air film is formed under the condition of reaching high rotating speed, so that the bearing is carried in the radial direction and the axial direction.

It can be understood that the first groove 721 is concavely formed on the outer sidewall of the journal 720, the second groove 621 is concavely formed on the end surface of the first thrust disk 620, and the third groove is concavely formed on the end surface of the second thrust disk 630, the depths of the first groove 721, the second groove 621, and the third groove are all h, and h is ≦ 0.005mm, for example, the depths of the first groove 721, the second groove 621, and the third groove may be 0.002mm, 0.005mm, and so on. It should be noted that the depth of the first groove 721 does not exceed the value range of the radial gap, and the depths of the second groove 621 and the third groove do not exceed the value range of the axial gap.

Because air can enter the radial gap from the axial gaps at the two ends of the shaft sleeve 610 respectively, that is, air flow can enter the radial gap along different directions, in the embodiment, the first grooves 721 on the shaft journal 720 are divided into two groups, and the two groups of the first grooves 721 are arranged at intervals, so that mutual interference of air flow between different groups is reduced; the first grooves 721 of one set communicate with the axial clearance at the first thrust disk 620 and the first grooves 721 of the other set communicate with the axial clearance at the second thrust disk 630.

Referring to the embodiment shown in fig. 6, two sets of first grooves 721 are separated at the middle position of the journal 720, and each first groove 721 is bent along the circumferential direction of the main shaft 700 to form a corner part, through which the direction of the airflow can be changed, so that a high pressure zone can be formed at the corner position, which is beneficial to increase the area of the high pressure zone and can provide greater radial bearing force.

Referring to the embodiment shown in fig. 7, the difference from the embodiment shown in fig. 6 is that each first groove 721 is curvedly continued in the circumferential direction at the outer side wall of the journal 720, and the first groove 721 has no corner portion and is substantially spiral-shaped. The gas flow enters the first recess 721 from the axial gap and forms a high pressure zone at the end position, so that a large radial load capacity can be increased.

It should be noted that, through the first groove 721, the second groove 621 and the third groove, a more significant dynamic pressure effect can be generated in the axial gap and the radial gap, so as to provide a greater axial bearing capacity and a greater radial bearing capacity, and the entire rotor system 800 can be stably supported to achieve high-speed operation.

It is understood that the first groove 721 is not limited to be disposed on the shaft journal 720, and the first groove 721 may be disposed on the inner wall of the shaft sleeve 610, specifically, the first groove 721 is disposed on the sidewall of each shaft sleeve unit 611 facing the main shaft 700, this embodiment is not shown in the drawings, and the specific structure of the first groove 721 can refer to the structure of the embodiment shown in fig. 6 and 7, and is not described herein again.

Referring to fig. 8, taking the first thrust disk 620 as an example for explanation, the second grooves 621 are uniformly distributed on the end face of the first thrust disk 620, the relationship between the minimum diameter g1 of the second grooves 621 on the first thrust disk 620 in the radial direction of the main shaft 700 and the inner diameter d of the shaft sleeve 610 satisfies g1 > d, and the circular dotted line shown in fig. 8 indicates the corresponding position of the inner side wall of the shaft sleeve 610 on the first thrust disk 620, and the diameter of the circular dotted line is the inner diameter d of the shaft sleeve 610. The air enters the axial gap from the edge of the first thrust disk 620 along the second grooves 621, the ends of the second grooves 621 approach the center of the first thrust disk 620, the ends of the plurality of second grooves 621 are circumferentially arranged to form a circle, and the positions of the ends of the second grooves 621 can be understood as the positions of the minimum diameters, that is, the ends of the second grooves 621 approaching the shaft body 710. It can be understood that if the end of the second groove 621 extends to the inner sidewall of the shaft sleeve 610, the air flow is directly communicated with the radial gap, and it is difficult to form a high pressure region in the second groove 621, which is not beneficial to generate a stable air film, so the diameter corresponding to the end of the second groove 621 is set to be larger than the inner diameter of the shaft sleeve 610 in the embodiment, so that the air flow can generate the high pressure region at the end of the second groove 621.

It should be noted that the second recess 621 is not limited to be disposed on the first thrust disk 620, and the second recess 621 may also be disposed on an end surface of the sleeve 610 facing the first thrust disk 620, where the embodiment is not shown in the drawings, and the specific structure of the second recess 621 may refer to the structure of the embodiment shown in fig. 5. Further, when the third groove is provided on the end face of the second thrust disk 630, the relationship between the minimum diameter g2 of the third groove in the radial direction on the second thrust disk 630 and the inner diameter d of the sleeve 610 satisfies g2 > d, see the structure of the second groove 621 in the above-described embodiment in particular. Of course, the third groove may also be disposed on the end surface of the shaft sleeve 610 facing the second thrust disk 630, which will not be described in detail.

In the embodiment, the first groove 721 may be formed on the journal 720 by a laser cutting and forming process, and meanwhile, the coating is performed, and the adopted coating material is preferably a wear-resistant material such as teflon, a Diamond-Like Carbon (DLC), and the Like, and the surface of the journal 720 has a strong wear resistance.

In addition, the shaft body 710 is provided with an annular groove 711 at a position connected with the magnetic ring 510, and glue is filled in the annular groove 711, so that the magnetic ring 510 is fixedly connected with the main shaft 700 through the glue, and the structure is firm and reliable. In operation, the stator 520 generates a changing magnetic field to drive the magnetic ring 510 to rotate, thereby enabling the rotor system 800 to operate at a high speed.

The embodiment of the utility model provides a cleaning device (not shown in the drawing) is still provided, and this cleaning device can be the dust catcher, specifically includes above embodiment the fan, the fan adopts bearing assembly 600 to do and replaces traditional ball bearing, can reduce the friction between main shaft 700 and the axle sleeve 610, is favorable to improving bearing assembly 600's life. The shaft sleeve 610 is of a split structure, after dynamic balance is manufactured, the shaft sleeve unit 611 is only needed to be assembled along the outer wall of the main shaft 700 to complete assembly of the shaft sleeve 610, the thrust assembly does not need to be disassembled and then sleeved into the shaft sleeve 610 from one side of the main shaft 700, influence of the assembly process of the shaft sleeve 610 on the residual unbalance amount of the rotor system 800 is effectively reduced, the problem of dynamic balance of the rotor system 800 is solved, and operation stability of the fan is improved.

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 without departing from the spirit of the present invention within the knowledge of those skilled in the art.

Claims (12)

1. Fan, its characterized in that includes:

a housing;

the main shaft is rotatably arranged in the shell;

an impeller connected with the main shaft;

the bearing assembly comprises a thrust assembly and a shaft sleeve sleeved on the spindle, the thrust assembly is arranged at the end part of the shaft sleeve along the axial direction of the spindle and is connected with the spindle, the shaft sleeve is fixedly connected with the shell, the shaft sleeve is in clearance fit with the spindle along the radial direction of the spindle, and the shaft sleeve is in clearance fit with the thrust assembly along the axial direction of the spindle;

the shaft sleeve comprises at least two shaft sleeve units, and the shaft sleeve units are assembled along the circumferential direction of the main shaft to form the shaft sleeve.

2. The fan as claimed in claim 1, wherein the housing is provided with a support frame, the support frame is sleeved outside the shaft sleeve, and each shaft sleeve unit is fixedly connected with an inner side wall of the support frame.

3. The fan as claimed in claim 2, further comprising a diffuser and a fan housing, wherein the diffuser is connected to the support frame, the fan housing is connected to the casing, an air inlet channel is formed between the impeller and the fan housing, and a diffuser channel communicated with the air inlet channel is formed between the diffuser and the fan housing.

4. The blower of claim 1, wherein the thrust assembly comprises a first thrust disk and a second thrust disk, the first thrust disk and the second thrust disk are respectively arranged at two ends of the shaft sleeve, and the first thrust disk and the second thrust disk are both fixedly connected with the spindle.

5. The fan of claim 4, wherein the main shaft comprises a shaft body and a journal, the journal having a diameter greater than a diameter of the shaft body, the shaft sleeve being disposed on the journal, and the first thrust disk and the second thrust disk being coupled to the shaft body.

6. The fan of claim 5, wherein a gap between the journal and the bushing is f, such that: f is (d-b)/2, and 0.002mm ≦ (d-b)/2 ≦ 0.01mm, wherein d is the inner diameter of the bushing and b is the diameter of the journal.

7. The fan of claim 5, wherein the outer side wall of the journal or the inner side wall of the shaft sleeve is provided with a plurality of first grooves, and the plurality of first grooves are arranged at intervals along the circumferential direction of the main shaft.

8. The fan according to claim 7, wherein a plurality of second grooves are disposed between the first thrust disk and the shaft sleeve, the plurality of second grooves are circumferentially spaced and distributed on an end surface of the first thrust disk or an end surface of the shaft sleeve along the main shaft, a plurality of third grooves are disposed between the second thrust disk and the shaft sleeve, and the plurality of third grooves are circumferentially spaced and distributed on an end surface of the second thrust disk or an end surface of the shaft sleeve along the main shaft.

9. The fan of claim 8, wherein the first, second, and third grooves are all h in depth, satisfying: h is less than or equal to 0.005 mm.

10. The fan according to claim 8, wherein when the second groove is formed in the end face of the first thrust disk, the second groove is located at a position with a minimum diameter g1 along the radial direction of the main shaft, and the minimum diameter g1 satisfies the following conditions: g1 > d; or when the third groove is arranged on the end face of the second thrust disk, the minimum diameter of the position of the third groove along the radial direction of the main shaft is g2, which satisfies the following conditions: g2 > d, and the inner diameter of the shaft sleeve is d.

11. The fan of claim 1 further comprising a stator and a rotor within the stator, the rotor being coupled to the spindle, the spindle having an outer peripheral wall provided with an annular groove for filling with glue, the annular groove being located at a junction of the spindle and the rotor.

12. Cleaning device, characterized in that it comprises a fan according to any of claims 1 to 11.

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