CN114718890B - Blower and cleaning device - Google Patents
Blower and cleaning device Download PDFInfo
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- CN114718890B CN114718890B CN202210410028.7A CN202210410028A CN114718890B CN 114718890 B CN114718890 B CN 114718890B CN 202210410028 A CN202210410028 A CN 202210410028A CN 114718890 B CN114718890 B CN 114718890B
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- sleeve
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- 238000004140 cleaning Methods 0.000 title claims abstract description 13
- 238000005452 bending Methods 0.000 claims description 25
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- 239000000428 dust Substances 0.000 description 9
- 238000009792 diffusion process Methods 0.000 description 8
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/08—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation
-
- A—HUMAN NECESSITIES
- A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
- A47L—DOMESTIC WASHING OR CLEANING; SUCTION CLEANERS IN GENERAL
- A47L5/00—Structural features of suction cleaners
- A47L5/12—Structural features of suction cleaners with power-driven air-pumps or air-compressors, e.g. driven by motor vehicle engine vacuum
- A47L5/22—Structural features of suction cleaners with power-driven air-pumps or air-compressors, e.g. driven by motor vehicle engine vacuum with rotary fans
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/053—Shafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/056—Bearings
- F04D29/057—Bearings hydrostatic; hydrodynamic
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/663—Sound attenuation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/668—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps damping or preventing mechanical vibrations
Abstract
The invention discloses a fan and cleaning equipment, which belong to the technical field of electrical equipment, wherein the fan comprises a shell, a main shaft, an impeller and a bearing assembly, the shell is provided with a support frame, and the support frame is provided with a mounting hole; the main shaft is rotationally arranged in the mounting hole; the impeller is connected with the main shaft; the bearing assembly comprises a shaft sleeve, the shaft sleeve is sleeved on the main shaft and is fixed in the mounting hole, the shaft sleeve is in clearance fit with the main shaft along the radial direction of the main shaft, the bearing assembly is adopted to replace a traditional ball bearing, and friction between the main shaft and the shaft sleeve can be reduced when the main shaft runs at a high speed; and increase elastic support spare at the lateral wall of axle sleeve, the axle sleeve passes through elastic support spare and is connected with the casing, and the vibration that the main shaft produced can transmit the axle sleeve, can consume the energy that the main shaft vibration produced through elastic support spare, helps suppressing the transmission of vibration, reduces the noise that the vibration produced, reaches the purpose of damping and making an uproar falls, improves fan running stability.
Description
Technical Field
The invention relates to the technical field of electrical equipment, in particular to a fan and cleaning equipment.
Background
The fan of the dust collector generates negative pressure at the inlet of the fan by rotating the impeller, thereby generating suction force for dust and the like. The rotating shaft of the traditional fan is generally supported by adopting a ball bearing, mechanical friction can be generated during the operation of the ball bearing, and particularly, the mechanical friction is more obvious after the rotating speed of the impeller is increased, so that the service life of the ball bearing is reduced.
In the related art, the fan adopts the gas bearing to replace the ball bearing, supports the rotating shaft through the radial bearing, can reduce the friction between the rotating shaft and the bearing, however, for the fan with ultrahigh rotating speed, because the rotating speed is higher and the effect of magnetic tension exists, the rotor can generate abnormal vibration and noise, and the running stability of the fan is reduced.
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, the shaft sleeve is adopted to form the gas bearing, so that the mechanical friction is reduced, the vibration energy of the rotor can be consumed, the purposes of vibration reduction and noise reduction are achieved, and the running stability of the fan is improved.
The invention further provides cleaning equipment comprising the fan.
According to an embodiment of the first aspect of the present invention, a fan includes:
the shell is provided with a supporting frame, and the supporting frame is provided with a mounting hole;
the main shaft is rotationally arranged in the mounting hole;
the impeller is connected with the main shaft;
the bearing assembly comprises a shaft sleeve, the shaft sleeve is sleeved on the main shaft and fixed in the mounting hole, the shaft sleeve is in clearance fit with the main shaft along the radial direction of the main shaft, and an elastic supporting piece connected with the supporting frame is arranged on the outer side wall of the shaft sleeve.
The fan provided by the embodiment of the invention has at least the following beneficial effects:
the fan drives the impeller to rotate at a high speed through the main shaft, a bearing assembly is adopted to replace a traditional ball bearing, the shaft sleeve and the main shaft are in clearance fit to form a gas bearing, and radial bearing force can be provided when the main shaft runs at a high speed so that the main shaft and the shaft sleeve can be separated, and friction between the main shaft and the shaft sleeve is reduced; and increase elastic support spare at the lateral wall of axle sleeve, the axle sleeve passes through elastic support spare and is connected with the casing, and the vibration that the main shaft produced can transmit the axle sleeve, can consume the energy that the main shaft vibration produced through elastic support spare, helps suppressing the transmission of vibration, reduces the noise that the vibration produced, reaches the purpose of damping and making an uproar falls, improves fan running stability.
According to some embodiments of the invention, the elastic support member is wrapped around the outer peripheral wall of the sleeve along the axial extension of the spindle, and the elastic support member is located between the outer peripheral wall of the sleeve and the inner peripheral wall of the mounting hole.
According to some embodiments of the invention, the thickness of the sleeve along the radial direction of the spindle is d, and the thickness of the elastic support is k, satisfying: k/d is more than or equal to 0.5 and less than or equal to 1.
According to some embodiments of the invention, the degree of stiffness of the resilient support is 40 degrees to 50 degrees.
According to some embodiments of the invention, the spindle comprises a spindle body and a shaft neck, the diameter of the shaft neck is larger than that of the spindle body, the shaft sleeve is sleeved on the shaft neck, a plurality of first grooves are formed in the outer peripheral wall of the shaft neck or the inner peripheral wall of the shaft sleeve, and the first 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 d1, the diameter of the journal is d2, and the gap between the journal and the bushing is f, satisfying: f= (d 1-d 2)/2 and 0.002mm < d1-d 2)/2 < 0.01mm.
According to some embodiments of the invention, the bearing assembly further comprises a first thrust plate fixed to an end of the journal in the axial direction of the spindle, and a second thrust plate fixed to an end of the journal remote from the first thrust plate, both the first and second thrust plates being in clearance fit with the sleeve in the axial direction.
According to some embodiments of the invention, a plurality of second grooves are arranged between the first thrust disc and the shaft sleeve, and the plurality of second grooves are arranged on the end face of the first thrust disc or the end face of the shaft sleeve at intervals along the circumferential direction of the main shaft; a plurality of third grooves are arranged between the second thrust disc and the shaft sleeve, and the third grooves are arranged on the end face of the second thrust disc or the end face of the shaft sleeve at intervals along the circumferential direction.
According to some embodiments of the invention, the depths of the first groove, the second groove and the third groove are all h, which satisfies: h is less than or equal to 0.005mm.
According to some embodiments of the invention, the inner diameter of the sleeve is d1, the outer diameter of the sleeve is d3, the plurality of second grooves are formed in the end face of the first thrust disk, the minimum diameter of the positions of the plurality of second grooves along the radial direction is phi 1, the plurality of third grooves are formed in the end face of the second thrust disk, the minimum diameter of the positions of the plurality of third grooves along the radial direction is phi 2, and the following conditions are satisfied: d1+ (d 3-d 1)/2 < φ1=φ2 < 0.5mm+d1+ (d 3-d 1)/2.
According to some embodiments of the invention, the first groove extends spirally along the axial direction of the main shaft, and a first bending groove is connected to one end of the first groove, which is far away from the end face of the shaft neck, along the axial direction of the main shaft.
According to some embodiments of the invention, the second groove and the third groove respectively extend along the circumferential direction of the main shaft in a spiral manner, one end, close to the axis of the main shaft, of the second groove along the radial direction of the main shaft is connected with a second bending groove, and one end, close to the axis of the main shaft, of the third groove along the radial direction of the main shaft is connected with a third bending groove.
A cleaning apparatus according to an embodiment of the second aspect of the present invention comprises a blower according to an embodiment of the first aspect described above.
The cleaning device provided by the embodiment of the invention has at least the following beneficial effects:
the fan of the embodiment is adopted by the cleaning equipment, and the bearing assembly is adopted to replace the traditional ball bearing, so that friction between the main shaft and the shaft sleeve can be reduced, and the service life of the bearing assembly is prolonged; and the elastic supporting piece is added on the outer side wall of the shaft sleeve, so that the damping effect can be provided through the elastic supporting piece, the energy generated by the vibration of the main shaft can be consumed, the transmission of the vibration can be restrained, the noise generated by the vibration can be reduced, the purposes of vibration reduction and noise reduction can be achieved, and the running stability of the cleaning equipment can be improved.
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 practice of the invention.
Drawings
FIG. 1 is a schematic diagram of an exploded construction of a blower according to an embodiment of the 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 a schematic cross-sectional view of a sleeve and an elastic support member according to an embodiment of the present invention;
FIG. 5 is a schematic cross-sectional view of a blower according to another embodiment of the invention;
FIG. 6 is a schematic view showing an assembled structure of a sleeve and an elastic support member according to another embodiment of the present invention;
FIG. 7 is a schematic view of the structure of an elastic support member according to another embodiment of the present invention;
FIG. 8 is a schematic view of the structure of an elastic support member according to another embodiment of the present invention;
FIG. 9 is a schematic cross-sectional view of a blower according to another embodiment of the invention;
FIG. 10 is a schematic view showing an assembled structure of a sleeve and an elastic support member according to another embodiment of the present invention;
FIG. 11 is an exploded view of a rotor system according to an embodiment of the present disclosure;
FIG. 12 is a schematic front view of a spindle and thrust assembly connection according to an embodiment of the present invention;
FIG. 13 is a perspective view of a spindle and thrust assembly connection according to an embodiment of the present invention;
FIG. 14 is a schematic front view of a first thrust plate according to an embodiment of the present invention;
fig. 15 is a schematic front view of a first thrust plate according to another embodiment of the present invention.
Reference numerals:
a blower 1000;
a rotor system 2000;
a fan housing 100; an air inlet 110;
an impeller 200; an air inlet channel 210; a mounting hub 220; a vane 230;
a diffuser 300; a diffuser passage 310;
a housing 400; a support frame 410; a mounting hole 411; a fixing groove 412;
A main shaft 500; a shaft body 510; annular groove 511; journal 520; a first groove 530; a first air inlet end 531; a first outlet end 532; a first bending groove 533;
a bearing assembly 600; a sleeve 610; an elastic support 611; a rubber strip 612; a first thrust plate 620; a second thrust plate 630; a third groove 631; a second groove 640; a second air intake 641; a second outlet port 642; a second bending groove 643;
a stator 700;
a magnetic ring 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 azimuth or positional relationship indicated by the terms upper, lower, etc. are based on the azimuth or positional relationship shown in the drawings, and are merely for convenience of description and simplification of the description, and are not indicative or implying that the apparatus or element in question must have a specific azimuth, be constructed and operated in a specific azimuth, and thus should not be construed as limiting the present invention.
In the description of the present invention, the description of the first and second is only for the purpose of distinguishing technical features, and should not be construed as indicating or implying relative importance or implying the number of technical features indicated or the precedence of the technical features indicated.
In the description of the present invention, it should be noted that terms such as arrangement, installation, connection, etc. should be construed broadly, and those skilled in the art may reasonably determine the specific meaning of the foregoing terms in the present invention in combination with the specific content 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. In this specification, schematic representations of the above terms do not necessarily refer to the same implementations or examples. 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 following description of the embodiments of the present invention will be made with reference to the accompanying drawings, in which it is apparent that the embodiments described below are some, but not all embodiments of the invention.
The fan 1000 according to the embodiment of the present invention is applied to a cleaning apparatus such as a vacuum cleaner, and particularly a product requiring an ultra-high rotation speed fan, and the fan 1000 will be described with reference to specific examples.
Referring to fig. 1 and 2, a fan 1000 provided in the embodiment includes a fan housing 100, an impeller 200, a diffuser 300, a casing 400, and a main shaft 500, a support frame 410 is disposed at a central position of the casing 400, the support frame 410 is provided with a mounting hole 411, the main shaft 500 is rotatably mounted in the mounting hole 411, the impeller 200 is connected with the main shaft 500, the fan housing 100 and the diffuser 300 are mounted at an upper end of the casing 400, the impeller 200 and the diffuser 300 are both located at an inner side of the fan housing 100, wherein an air inlet 110 is formed on the fan housing 100, an air inlet channel 210 is formed between the impeller 200 and the fan housing 100, the diffuser 300 is fixedly connected with the support frame 410, a diffusion channel 310 communicated with the air inlet channel 210 is formed between the diffuser 300 and the fan housing 100, the impeller 200 rotates at a high speed to generate an air flow, and the air flow enters the air inlet channel 210 from the air inlet 110 and is diffused through the diffusion channel 310, so that the pressure of the air flow is increased to increase the generation of the fan 1000.
Taking the dust collector as an example, under the action of negative pressure generated by the fan 1000, the dust, garbage and other foreign matters can be sucked into a filter cloth bag or other processing structures of the dust collector to finish dust collection and other works, and the specific structure of the dust collector is not shown in the drawings.
Fig. 2 is a schematic cross-sectional structure of a fan 1000 according to an embodiment of the present invention, a bearing assembly 600 for supporting a main shaft 500 is further disposed in a casing 400, the bearing assembly 600 includes a sleeve 610, the sleeve 610 is sleeved on the main shaft 500, the sleeve 610 is fixed in a mounting hole 411 of a supporting frame 410, a clearance fit is formed between the sleeve 610 and the main shaft 500, that is, a clearance is formed between the sleeve 610 and the main shaft 500, and the sleeve 610 can be understood as a radial bearing of the main shaft 500. It will be appreciated that the dynamic pressure effect will form in the sleeve 610 when the spindle 500 is rotated at high speed to generate a gas film, and the radial support is provided to the spindle 500 by the gas film pressure, so that the spindle 500 can stably operate.
Referring to fig. 2, the bearing assembly 600 further includes a thrust assembly disposed at an axial end of the shaft sleeve 610, the thrust assembly being fixedly coupled to the spindle 500, the thrust assembly being in a clearance fit with the shaft sleeve 610, the thrust assembly being understood to be a thrust bearing of the spindle 500, and the thrust assembly being disposed at one or both ends of the shaft sleeve 610 in the axial direction. Gaps are formed between the shaft sleeve 610 and the main shaft 500 and between the shaft sleeve 610 and the thrust component, so that the shaft sleeve 610 and the thrust component are matched to form a gas bearing, also called an air bearing, and the main shaft 500 can support the main shaft 500 when rotating at a high speed, so that the main shaft 500 can stably operate.
It should be noted that, the thrust assembly is fixedly connected with the spindle 500, the sleeve 610 is fixedly connected with the support frame 410, the thrust assembly can rotate along with the spindle 500, and the sleeve 610 is fixed. When the main shaft 500 rotates at a high speed, an air film is formed after air pressure is stabilized in a gap between the shaft sleeve 610 and the main shaft 500 and a gap between the shaft sleeve 610 and the thrust assembly, thereby generating a dynamic pressure effect, and a bearing force can be provided to the main shaft 500 in both axial and radial directions to support the main shaft 500 to rotate at a high speed, so that the main shaft 500 can float and be separated from the shaft sleeve 610.
The traditional fan uses the ball bearing to support the main shaft, and mechanical friction can be generated during the operation of the ball bearing, and particularly, the mechanical friction is more obvious after the rotation speed is increased, so that the mechanical efficiency is obviously reduced, vibration and noise are generated, and the service life of the bearing is shorter. Compared with the traditional fan, the fan 1000 of the embodiment of the invention uses the gas bearing to replace the ball bearing, and utilizes the gas film to provide radial bearing force to support the main shaft 500 to rotate at high speed, so that the friction between the main shaft 500 and the shaft sleeve 610 is reduced, the service life of the bearing assembly 600 is prolonged, and the performance and mechanical noise of the fan 1000 are effectively improved; the gas bearing can provide higher radial and axial bearing force, the rotation precision is higher, the power loss is reduced to the minimum while the high-rotation-speed operation is performed, the rotation speed can reach more than 100000 revolutions per minute, and the high-suction requirement of cleaning equipment such as dust collectors is met.
Referring to fig. 1 and 2, the blower 1000 of the embodiment further includes a stator 700, a rotor, and an electric control board 900. The rotor is installed at the lower end of the main shaft 500, i.e., the end of the main shaft 500 away from the impeller 200, the stator 700 is fixed in the housing 400, the stator 700 is disposed around the outer circumference of the rotor, and the stator 700 and the rotor are engaged to drive the main shaft 500 to rotate, thereby driving the impeller 200 to rotate at a high speed. An electric control board 900 is mounted on the stator 700 or the casing 400, and the electric control board 900 is used for controlling the fan 1000.
Referring to fig. 3, the rotor includes a magnetic ring 800, the magnetic ring 800 is connected with a main shaft 500, an upper end of the main shaft 500 is connected with an impeller 200, a lower end is connected with the magnetic ring 800, a bearing assembly 600 is installed at a middle position of the main shaft 500, an axial height of a shaft sleeve 610 is smaller than that of the main shaft 500, the shaft sleeve 610 is sleeved on an outer side wall of the main shaft 500, and a thrust assembly includes thrust structures at upper and lower ends of the shaft sleeve 610, wherein the thrust structures may be discs, discs or other shaped thrust members. In the embodiment, the impeller 200, the main shaft 500, the bearing assembly 600 and the magnetic ring 800 are formed into a rotor system 2000, and fig. 3 is a schematic cross-sectional structure of the rotor system 2000.
It can be understood that, for the fan 1000 with ultra-high rotation speed, the stator 700 and the rotor cooperate to drive the main shaft 500 to rotate at high speed, and the main shaft 500 is easy to generate vibration and noise due to the magnetic tension force generated by the stator 700 on the rotor, so that the elastic supporting member 611 is added on the outer side wall of the shaft sleeve 610 according to the embodiment of the invention, the elastic supporting member 611 can provide damping effect, reduce the noise generated by vibration, achieve the purpose of vibration reduction and noise reduction, and enable the rotor system 2000 to stably operate at high rotation speed.
Referring to fig. 2 and 3, in some embodiments, the support frame 410 is substantially in a sleeve shape, a through hole in the center of the support frame 410 is a mounting hole 411, the mounting hole 411 is matched with the shaft sleeve 610, the shaft sleeve 610 is located in the mounting hole 411, the elastic support member 611 is disposed on an outer side wall of the shaft sleeve 610, the shaft sleeve 610 is fixedly connected with the support frame 410 through the elastic support member 611, so that the shaft sleeve 610 can be fixed in the mounting hole 411, and the spindle 500 can rotate in the shaft sleeve 610.
The elastic supporting member 611 is understood as a buffer member made of an elastic material, and can connect the shaft sleeve 610 and the supporting frame 410, and can provide a damping effect. In the embodiment shown in fig. 2 and 3, the elastic supporting member 611 may be made of rubber, and the elastic supporting member 611 may be adhered between the shaft sleeve 610 and the supporting frame 410, so that the shaft sleeve 610 and the supporting frame 410 are elastically connected. Vibration generated when the main shaft 500 rotates at a high speed is transmitted to the shaft sleeve 610, the elastic support 611 generates damping effect between the shaft sleeve 610 and the support frame 410, and it can be understood that the capability of transmitting vibration of the structure can be reduced through the damping effect, that is, the elastic support 611 can consume energy generated by vibration of the main shaft 500, so that the transmission of the vibration is restrained, noise generated by the vibration is reduced, the purpose of vibration reduction and noise reduction is achieved, the running performance of the rotor system 2000 is improved, and the running stability of the fan 1000 is improved.
Referring to fig. 4, fig. 4 is a schematic cross-sectional view of the elastic support 611 wrapped around the outer side of the sleeve 610, specifically, the elastic support 611 is made of rubber, the outer circumferential wall of the sleeve 610 is covered with the rubber to form a buffer, and then the sleeve 610 is fixed together with the elastic support 611 into the mounting hole 411.
It should be noted that, the elastic supporting member 611 is not limited to be made of rubber, and an elastic structure made of metal may be used, for example, a metal wire is compressed to form a metal buffer member with a certain elasticity, and the metal buffer member is connected between the shaft sleeve 610 and the supporting frame 410; the elastic support 611 may also be made of other elastic materials, such as a high damping composite material, etc., without being limited thereto. The elastic supporting members 611 may be disposed at two ends or in the middle of the outer side wall of the shaft sleeve 610 in the axial direction, and the elastic supporting members 611 may be connected to the shaft sleeve 610 and the supporting frame 410 by means of glue bonding or the like.
Referring to fig. 2 and 3, in some embodiments, the support frame 410 is provided to have a height close to that of the boss 610, the elastic support 611 is wrapped around the outer circumferential wall of the boss 610, the hole diameter of the mounting hole 411 is larger than the outer diameter of the boss 610, the boss 610 is fitted into the mounting hole 411, the elastic support 611 is located between the outer circumferential wall of the boss 610 and the inner circumferential wall of the mounting hole 411, the elastic support 611 has a substantially cylindrical shape, the radially outer circumferential wall of the elastic support 611 is fitted to the inner circumferential wall of the mounting hole 411, and the inner circumferential wall of the elastic support 611 is fitted to the outer circumferential wall of the boss 610, thereby fixing the boss 610 in the mounting hole 411. In the embodiment, an annular groove can be formed in the inner peripheral wall of the mounting hole 411, and glue is filled in the annular groove, so that the elastic supporting piece 611 can be fastened on the inner peripheral wall of the mounting hole 411, and the assembly structure is firmer and more reliable.
Referring to fig. 4, it can be understood that the outer peripheral wall of the shaft sleeve 610 is fixedly connected with the supporting frame 410 through the elastic supporting member 611, so that damping can be provided for the shaft sleeve 610 in the circumferential direction, the inner peripheral wall of the shaft sleeve 610 is in clearance fit with the spindle 500, and when the spindle 500 rotates at a high speed, the damping generated by the elastic supporting member 611 can consume the energy generated by the vibration of the shaft sleeve 610, so that the transmission of the vibration to the casing 400 is effectively reduced, the vibration and noise reduction effects are achieved, and the rotor system 2000 operates more stably.
Referring to fig. 5 and 6, in some embodiments, the elastic support 611 is a metal buffer made of metal wire, and has a generally circular shape as a whole. Fig. 5 is a schematic cross-sectional structure of the metal buffer member assembled into the fan 1000, and fig. 6 is a schematic diagram of the metal buffer member assembled with the casing 400. Specifically, a plurality of wires are wound together and shaped to form an annular structure, and fig. 7 is a schematic diagram of the overall structure of the metal buffer member, and because a certain gap exists between the wires, the buffer member has certain elasticity, has high damping characteristics, and can provide an effective damping vibration attenuation effect. In addition, the metal buffer member is annular and circumferentially wraps the shaft sleeve 610, the inner peripheral wall of the metal buffer member is attached to the outer peripheral wall of the shaft sleeve 610, the contact area is larger, and vibration energy is absorbed more favorably.
It should be noted that, referring to fig. 6, when assembling, the elastic supporting member 611 may be fixed in the mounting hole 411, and then the rotor system 2000 may be integrally assembled in the mounting hole 411, so that the shaft sleeve 610 is correspondingly and fixedly connected with the elastic supporting member 611, and the elastic supporting member 611 may be fixed between the supporting frame 410 and the shaft sleeve 610 by means of glue bonding or interference fit, so that when the spindle 500 rotates at a high speed, energy generated by vibration can be consumed through interaction of the elastic supporting member 611 and the vibration wave, transmission of the vibration is effectively reduced, and an effective vibration and noise reduction effect is achieved.
It can be appreciated that the elastic supporting member 611 may also be made of rubber instead of metal buffering members, as shown in fig. 8, the elastic supporting member 611 is made of rubber, and has a circular ring shape as a whole, and the specific material may be nitrile rubber, etc., which has the characteristics of better elasticity, heat resistance, etc., and can provide better damping and vibration reducing effects, and the assembly mode of the rubber buffering member may refer to the structure of the embodiment shown in fig. 6, and is not described in detail.
Referring to fig. 9, fig. 9 is a schematic cross-sectional structure of a rubber buffer member assembled into a fan 1000, the rubber buffer member is annular and circumferentially wraps a shaft sleeve 610, an inner peripheral wall of the rubber buffer member is attached to an outer peripheral wall of the shaft sleeve 610, and energy generated by vibration can be consumed through interaction of the rubber buffer member and vibration waves, so that transmission of the vibration is effectively reduced, and an effective vibration and noise reduction effect is achieved.
Referring to fig. 10, in some embodiments, a plurality of fixing grooves 412 may be provided on an inner wall of the mounting hole 411, the fixing grooves 412 may be spaced apart along a circumference of the mounting hole 411, and the fixing grooves 412 may extend in an axial direction such that a height of the fixing grooves 412 in the axial direction may be close to a height of the shaft sleeve 610, a rubber strip 612 may be provided in each fixing groove 412, the plurality of rubber strips 612 may be distributed in the circumferential direction and may be connected to an outer circumferential wall of the shaft sleeve 610, that is, the elastic support 611 may include a plurality of rubber strips 612, and each rubber strip 612 may absorb vibration energy of the shaft sleeve 610 through contact of the plurality of rubber strips 612 with the shaft sleeve 610, thereby achieving a vibration reduction purpose. It can be appreciated that the rubber strips 612 can be adhered in the fixing groove 412 by glue, the greater the number of the rubber strips 612, the better the vibration damping effect, and the specific number can be set according to the actual requirement, and is not limited.
It should be noted that, the elastic supporting member 611 provides a damping effect through its own elasticity, the thickness and hardness of the elastic supporting member 611 both affect the damping effect, the thickness of the elastic supporting member 611 is too small or the hardness is too high, the vibration absorbing effect is reduced, and the vibration and noise reduction is not obvious; if the thickness of the elastic support 611 is too large or too small, the sleeve 610 and the support frame 410 are easily collapsed to interfere with each other.
Thus, in the embodiment, the radial thickness of the side wall of the sleeve 610 is d, and the radial thickness of the elastic support 611 is k, which satisfies the following conditions: 0.5.ltoreq.k/d.ltoreq.1, it being understood that the minimum thickness of the elastic support 611 is half the wall thickness of the sleeve 610, and the maximum thickness of the elastic support 611 is equal to the thickness of the sleeve 610. The radial thickness of the sidewall of the sleeve 610 is calculated according to the outer diameter and the inner diameter of the sleeve 610, for example, the sleeve 610 has an outer diameter of 12mm and an inner diameter of 6mm, the sleeve 610 has a wall thickness of 3mm, and the thickness of the elastic support 611 may be 1.5mm, 2mm, 3mm, etc. In the embodiment, the hardness of the elastic supporting member 611 is smaller than that of the shaft sleeve 610, so as to play a role of damping. Taking the measurement of the shore hardness as a reference standard, the shore hardness degree of the elastic supporting member 611 is 40-50 degrees, for example, the shore hardness degree may be 40 degrees, 45 degrees, 50 degrees, etc., so that the elastic supporting member 611 is not excessively hard or excessively soft, and an effective vibration absorbing effect can be provided.
Referring to fig. 1 and 2, in the embodiment, the diffuser 300 is sleeved outside the support frame 410, and the diffuser 300 is located at one end of the support frame 410 near the impeller 200. The casing 400 may further fix the diffuser 300 by a fastening structure (not shown in the drawings), so that the diffuser 300 can be stably mounted on the casing 400. In addition, the support frame 410 and the casing 400 are integrally formed, so that the overall assembly strength of the rotor system 2000 and the casing 400 can be improved, and the structure is stable and reliable.
Referring to fig. 1, the diffuser 300 includes a mounting hub 220 and blades 230 circumferentially distributed along the mounting hub 220, wherein the mounting hub 220 is fixedly coupled to a support frame 410, and a diffuser passage 310 is defined between the mounting hub 220, the blades 230, and the fan housing 100, and the diffuser passage 310 may be understood as a primary diffuser passage. In some embodiments, a diffusion structure may be further added in the casing 400, and a second-stage diffusion channel that is in communication with the first-stage diffusion channel may be defined by the diffusion structure, so that the airflow can be sequentially diffused through the first-stage diffusion channel and the second-stage diffusion channel after passing through the air inlet channel 210, so that the pressure of the airflow is further improved, and the suction force is improved.
Referring to fig. 11, fig. 11 is a schematic diagram illustrating an exploded structure of a rotor system 2000 according to an embodiment of the present invention. In the embodiment, the shaft sleeve 610 is integrally in a ring shape, the main shaft 500 comprises a shaft body 510 and a shaft neck 520, the shaft neck 520 is positioned in the middle of the shaft body 510, the diameter of the shaft neck 520 is larger than that of the shaft body 510, the impeller 200 and the magnetic ring 800 are respectively connected to the upper end and the lower end of the shaft body 510, and the shaft sleeve 610 is sleeved on the shaft neck 520.
Referring to fig. 11, in some embodiments, the thrust assembly includes a first thrust plate 620 and a second thrust plate 630, each of the first thrust plate 620 and the second thrust plate 630 is in a disc shape and fixed on the main shaft 500, and the first thrust plate 620 and the second thrust plate 630 are respectively located at both ends of the sleeve 610 in the axial direction. Wherein, the first thrust disc 620 is located at one end of the main shaft 500 near the impeller 200, and the first thrust disc 620 is in clearance fit with the shaft sleeve 610; the second thrust plate 630 is located at one end of the main shaft 500 near the magnetic ring 800, and the second thrust plate 630 is in clearance fit with the shaft sleeve 610. In addition, an annular groove 511 is formed in the shaft body 510 and connected with the magnetic ring 800, and glue is filled in the annular groove 511, so that the magnetic ring 800 is fixedly connected with the shaft body 510 through the glue, and the structure is firm and reliable.
It should be noted that, as shown in fig. 11, the shaft sleeve 610 is sleeved on the journal 520, the impeller 200 and the magnetic ring 800 are respectively connected to the shaft body 510, the first thrust disk 620 and the second thrust disk 630 are tightly attached to the end surface of the journal 520 along the axial direction, and the length of the shaft sleeve 610 may be slightly smaller than the length of the journal 520, so that the first thrust disk 620 and the second thrust disk 630 are positioned in the axial direction through the journal 520, so that a certain gap can be separated between the first thrust disk 620 and the second thrust disk 630 and the shaft sleeve 610, thereby forming a thrust bearing.
Referring to fig. 12 and 13, it can be appreciated that the main shaft 500 is connected with the first thrust plate 620 and the second thrust plate 630 to form a unitary structure, which is beneficial to reducing assembly errors of the thrust assembly, maintaining the main shaft 500 to have high coaxiality with the bearing assembly 600, and the first thrust plate 620 and the second thrust plate 630 cooperate with the shaft sleeve 610 to form a gas bearing, which can provide high radial and axial rotation precision for the main shaft 500. It should be noted that, the first thrust plate 620 and the second thrust plate 630 may be connected to the main shaft 500 by glue, or may be formed by interference fit, welding, etc., which is not limited herein.
Referring to fig. 3, it can be understood that the gap between the spindle 500 and the sleeve 610 is a radial gap, and the radial gap needs to satisfy that when the spindle 500 rotates at a high speed, the air pressure between the spindle 500 and the sleeve 610 can form a stable air film, the spindle 500 is radially supported by the air film forming dynamic pressure effect, the air film thickness forms a wedge shape in the circumferential direction, and a high pressure region is generated at a position where the air film thickness is smaller, and radial bearing force is provided to the spindle 500 by the high pressure region.
It is considered that the stability of the air film is affected in the case where the gap between the main shaft 500 and the sleeve 610 is too small or too large. The radial clearance is one of the main factors affecting the static bearing capacity of the radial bearing, and the smaller the radial clearance, the greater the bearing capacity, and the radial bearing can provide a greater centripetal force, so that the fan 1000 can operate at a higher rotational speed; however, the radial clearance is too small, the radial clearance cannot be ensured due to errors in machining and assembly, and the shaft sleeve 610 is easily expanded and deformed due to friction and heat generated during high-speed rotation, so that the clearance is reduced, and the main shaft 500 and the shaft sleeve 610 possibly collide, and once the main shaft 500 is collided, the main shaft 500 and the shaft sleeve 610 are easily deformed and are blocked and fail due to high kinetic energy of the main shaft 500 at high rotation speed.
Based on the above consideration, in the embodiment, as shown in fig. 3, the inner diameter of the shaft sleeve 610 is d1, the diameter of the journal 520 is d2, the gap between the journal 520 and the shaft sleeve 610 is f= (d 1-d 2)/2, and 0.002mm (d 1-d 2)/2 is less than or equal to 0.01mm, that is, the value of the radial gap between the journal 520 and the shaft sleeve 610 is in the range of 0.002mm to 0.01mm (millimeter), which is favorable for forming a stable air film in the radial gap. For example, the radial clearance may be 0.002mm, 0.005mm, 0.01mm, etc.; as another specific example, the inner diameter of the sleeve 610 is 8.120mm, the diameter of the journal 520 is 8.110mm, and a radial clearance of 0.005mm is obtained.
The clearance between the sleeve 610 and the first thrust disk 620 and the second thrust disk 630 is an axial clearance, and the axial clearance may be the same as or different from the radial clearance. In some preferred embodiments, the radial gap has a value of 0.002mm-0.006mm and the axial gap has a value of about 0.004mm.
In addition, the radial bearing capacity generated by the shaft sleeve 610 is positively correlated with the diameter of the shaft sleeve 610, and the larger the diameter is, the larger the bearing area is, and the larger the bearing capacity is; however, as the diameter increases, the mass of the main shaft 500 increases, so that the bearing capacity required for supporting the main shaft 500 increases, and thus, as shown in fig. 3, the outer diameter of the sleeve 610 is d3, and the outer diameter of the mounting hub 220 of the impeller 200 is d4, so that: d3/d4 is more than or equal to 0.2 and less than or equal to 0.4.
Referring to fig. 12, in some embodiments, the outer circumferential wall of the journal 520 is provided with a plurality of first grooves 530, and the plurality of first grooves 530 extend spirally along the axial direction of the spindle 500. Specifically, the first grooves 530 include a first air inlet end 531 and a first air outlet end 532, where the first air inlet end 531 is located at an edge of the journal 520, the first air inlet end 531 extends obliquely along a circumferential direction, and the extending direction is opposite to the rotating direction of the spindle 500, for example, when the rotating direction of the impeller 200 is clockwise, the extending direction of the plurality of first grooves 530 inclines around the counterclockwise direction, so that the air flow can more easily enter from the first air inlet end 531 of the first grooves 530, and the air film is formed at the first air outlet end 532 of the first grooves 530, which is beneficial to quickly generating the dynamic pressure effect.
As shown in fig. 12, the plurality of first grooves 530 extend in a curved manner along the circumferential direction of the main shaft 500, and have a substantially spiral shape. It will be appreciated that a radial air gap is formed between the outer peripheral wall of the journal 520 and the inner peripheral wall of the sleeve 610, and during high-speed rotation of the spindle 500, air can enter the radial air gap from the first groove 530 and form a high-pressure region at the first air outlet end 532 of the first groove 530, and since the first groove 530 is uniformly arranged along the circumferential direction, a uniformly distributed high-pressure region can be generated, and the pressure generated by the high-pressure region helps to form a stable air film, and radial bearing force is generated on the spindle 500, so that the journal 520 is completely separated from the sleeve 610, and the rotor system 2000 is more stable during high-speed operation, and the performance and mechanical noise of the fan 1000 are improved.
It should be noted that, since air can enter the radial air gap from the positions at the two ends of the sleeve 610, in the embodiment shown in fig. 12, a plurality of first grooves 530 are respectively disposed at the two ends of the journal 520 along the axial direction, so that the first grooves 530 on the journal 520 are separated into two groups, which is beneficial to providing a more stable radial bearing force for the spindle 500.
Referring to fig. 13, in some embodiments, each first groove 530 is connected to a first bending groove 533 at a first air outlet end 532, where the connection position between the first groove 530 and the first bending groove 533 has a corner position, the connection between the first groove 530 and the first bending groove 533 is a substantially V-shaped groove, and the first bending groove 533 may also be understood as an extension of the first groove 530. It will be appreciated that when the air flow enters the first groove 530 from the first air inlet end 531 and passes through the first bending groove 533, the direction of the air flow can be changed, so that the air flow forms a high pressure region at the connection between the first groove 530 and the first bending groove 533, and the area of the high pressure region can be increased by the first bending groove 533, so as to further provide radial bearing capacity. It should be noted that, in the embodiment shown in fig. 13, the first grooves 530 are arranged in two groups at two ends of the journal 520, and the two groups of first grooves 530 are separated at the middle position of the journal 520, so as to reduce the interference of the air flow between the different groups of first grooves 530.
Referring to fig. 4, as another embodiment, a plurality of first grooves 530 may be provided in the inner circumferential wall of the sleeve 610. When the spindle 500 rotates at a high speed, air can also enter the radial air gap and form a high pressure area at the connection between the first groove 530 and the first bending groove 533, the pressure generated by the high pressure area helps to form a stable air film, and radial bearing force is generated on the spindle 500, so that the journal 520 is completely separated from the shaft sleeve 610, the rotor system 2000 is more stable during high-speed operation, and the performance and mechanical noise of the fan 1000 are improved. The specific form of the first groove 530 can be seen in the structure of the embodiment shown in fig. 12 and 13, and will not be described here.
Referring to fig. 11 and 13, in some embodiments, a plurality of second grooves 640 are provided on an end surface of the first thrust plate 620 facing the shaft sleeve 610, a plurality of third grooves 631 are provided on an end surface of the second thrust plate 630 facing the shaft sleeve 610, and the plurality of second grooves 640 and the plurality of third grooves 631 are all circumferentially spaced apart, and a specific description will be given below taking the first thrust plate 620 as an example.
Referring to fig. 14, fig. 14 is a schematic front view of a first thrust plate 620 according to an embodiment. The plurality of second grooves 640 extend spirally along the circumference of the main shaft 500, and each second groove 640 also includes a second air inlet end 641 and a second air outlet end 642, wherein the second air inlet end 641 of the second groove 640 is located along the outer circumference of the first thrust disk 620, the second air inlet end 641 extends obliquely along the circumference, and the extending direction is opposite to the rotating direction of the main shaft 500, for example, when the rotating direction of the impeller 200 is clockwise, the extending direction of the plurality of second grooves 640 extends obliquely along the counterclockwise direction, so that air flow can more easily enter from the second air inlet end 641 of the second groove 640, and the air flow can quickly generate dynamic pressure effect to form an air film at the second air outlet end 642 of the second groove 640. The plurality of first grooves 530 extend in a curved manner along the circumferential direction of the main shaft 500, and have a substantially spiral shape. An axial air gap is formed between the first thrust disc 620 and the shaft sleeve 610, and in the process of high-speed rotation of the main shaft 500, air can enter the axial air gap from the second groove 640 and form a high-pressure area at the second air outlet end 642 of the second groove 640, pressure generated by the high-pressure area is favorable for forming a stable air film, an axial bearing force is generated on the main shaft 500, the axial bearing force can limit the main shaft 500 along the axial direction, and the rotor system 2000 is supported by matching with the radial bearing force, so that the rotor system 2000 operates more stably, and the stability of the fan 1000 is further improved.
Referring to fig. 15, fig. 15 is a schematic front view of a first thrust plate 620 according to another embodiment. Each second groove 640 is connected to a second bending groove 643 at the second air outlet end 642, the second groove 640 is connected to the second bending groove 643 to form a V-shaped groove, and the second bending groove 643 may also be understood as an extension of the second groove 640. It can be appreciated that when the air flow enters the second groove 640 from the second air inlet end 641 and passes through the second bending groove 643, the direction of the air flow can be changed, so that a high pressure area is formed at the connection position of the second groove 640 and the second bending groove 643, the area of the high pressure area can be increased through the second bending groove 643, and the axial bearing capacity is further provided.
In the embodiment, for the specific shape and the distribution structure of the third groove 631, reference may be made to the implementation manner of the second groove 640, and similarly, a third bending groove (not shown in the drawing) may be connected to the air outlet end of the third groove 631 to increase the area of the high pressure area on the end face of the second thrust disc 630, which is not described herein in detail. It will be appreciated that air can enter the axial gap at both ends of the sleeve 610 along the second groove 640 and the third groove 631 and enter the radial gap from the axial gap, thereby enabling the formation of high pressure regions in the axial gap and the radial gap, respectively, and a stable air film to be formed in the event that a high rotational speed is reached, so that the spindle 500 is carried in both the radial and axial directions, and the rotor system 2000 operates more stably.
It will be appreciated that the first groove 530 is formed on the outer sidewall of the journal 520, the second groove 640 is recessed on the end surface of the first thrust disk 620, and the third groove 631 is recessed on the end surface of the second thrust disk 630, the depths of the first groove 530, the second groove 640 and the third groove 631 are increased, which is advantageous for improving the damping and stability of the rotor system 2000; however, too large a depth can result in an increased equivalent gap and reduced radial and axial bearing forces, providing reduced centripetal forces, which are detrimental to high rotational speed operation of the rotor. Accordingly, the depths of the first groove 530, the second groove 640 and the third groove 631 are all h in the embodiment, and h is less than or equal to 0.005mm, for example, the depths of the first groove 530, the second groove 640 and the third groove 631 may be 0.002mm, 0.005mm, etc. It should be noted that the depth of the first groove 530 does not exceed the range of the radial gap, and the depths of the second groove 640 and the third groove 631 do not exceed the range of the axial gap.
It should be noted that, for the rotor system 2000, the first grooves 530, the second grooves 640 and the third grooves 631 can generate a more obvious dynamic pressure effect in the axial gap and the radial gap, so as to provide a greater axial bearing force and radial bearing force, and can stably support the entire rotor system 2000 to realize high-speed operation.
Referring to fig. 14 and 15, taking the first thrust plate 620 as an example, the plurality of second grooves 640 are uniformly distributed on the end surface of the first thrust plate 620, the relationship between the minimum diameter Φ1 of the plurality of second grooves 640 along the radial direction of the spindle 500 on the first thrust plate 620 and the inner diameter d1 of the sleeve 610 satisfies Φ1 > d1, and the circular dotted line shown in fig. 14 and 15 indicates the corresponding position of the inner sidewall of the sleeve 610 on the first thrust plate 620, and the diameter of the circular dotted line is the inner diameter d1 of the sleeve 610. It will be appreciated that air enters the axial gap from the edge of the first thrust disk 620 along the second groove 640, and the second air outlet ends 642 of the second groove 640 are close to the center of the first thrust disk 620, and the second air outlet ends 642 of the plurality of second grooves 640 are located at the same radial position, which not only facilitates processing, but also enables the high pressure regions of the second grooves 640 to be uniformly distributed in the circumferential direction, providing a more stable axial bearing force. The location of the second air outlet end 642 of the second groove 640 can be understood as the minimum diameter location.
It can be appreciated that if the second air outlet end 642 of the second groove 640 extends to the inner side wall of the shaft sleeve 610, the air flow is directly communicated with the radial gap, so that a high pressure region is difficult to form in the second groove 640, which is unfavorable for generating a stable air film, so that in the embodiment, the diameter of the position of the second air outlet end 642 of the second groove 640 is set to be larger than the inner diameter of the shaft sleeve 610, so that the air flow can generate a high pressure region at the second air outlet end 642. It should be noted that, when the second air outlet end 642 of the second groove 640 is connected to the second bending groove 643, the minimum diameter of the position of the second bending groove 643 is the minimum diameter of the second groove 640.
It should be noted that, in the case that the number of the second grooves 640 on the first thrust plate 620 is not changed and satisfies Φ1 > d1, the longer the second grooves 640 extend in the radial direction, the larger the second grooves 640 occupy, and it is understood that when the area of the second grooves 640 is too large, the equivalent gap between the first thrust plate 620 and the sleeve 610 increases and the bearing capacity decreases. When the area of the second groove 640 is too small, the high pressure area generated by the second groove 640 has a limited effect, which is disadvantageous in improving the stability of the rotor system 2000. Based on this, in the embodiment, the inner diameter d1, the outer diameter d3, and the minimum diameter Φ1 of the sleeve 610 are further optimized to satisfy: d1+ (d 3-d 1)/2 < phi 1 < 0.5mm+d1+ (d 3-d 1)/2, effectively avoiding too small or too large a region of the second groove 640, facilitating the formation of an effective groove region on the first thrust disk 620, and making the rotor system 2000 more stable in operation.
It should be noted that, the second groove 640 is not limited to being disposed on the first thrust plate 620, and the second groove 640 may be disposed on an end surface of the sleeve 610 facing the first thrust plate 620, which is not illustrated in the drawings. Further, when the third groove 631 is provided on the end face of the second thrust plate 630, the relationship between the minimum diameter Φ2 of the third groove 631 in the radial direction on the second thrust plate 630 and the inner diameter d1 of the boss 610 satisfies Φ2 > d1. And in some preferred embodiments, the inner diameter d1, outer diameter d3, and minimum diameter Φ2 of the sleeve 610 satisfy: d1+ (d 3-d 1)/2 < phi 2 < 0.5mm+d1+ (d 3-d 1)/2, which facilitates forming an effective groove area on the second thrust disk 630 that makes the rotor system 2000 more stable in operation, see in particular the structure of the second groove 640 in the above embodiment. Of course, the third groove 631 may also be disposed on an end surface of the shaft sleeve 610 facing the second thrust plate 630, which will not be described herein.
It should be noted that, in the embodiment, the first groove 530 may be formed on the journal 520 by a process such as laser cutting molding or electro-erosion, and the plating process may be performed at the same time, and the plating material used is preferably a wear-resistant material such as teflon, diamond-Like Carbon (DLC), so that the surface of the journal 520 has a relatively strong wear resistance. Meanwhile, the second groove 640 and the third groove 631 may be formed on the first thrust plate 620 and the second thrust plate 630 by the above process, which is not described in detail.
Embodiments of the present invention also provide a cleaning apparatus (not shown in the drawings), which may be a dust collector, specifically including the blower 1000 described in the above embodiments, where the blower 1000 employs the bearing assembly 600 as a substitute for a conventional ball bearing, so that friction between the main shaft 500 and the shaft sleeve 610 can be reduced, which is beneficial for improving the service life of the bearing assembly 600. In the embodiment, the elastic supporting member 611 is added on the outer side wall of the shaft sleeve 610, so that energy generated by vibration of the main shaft 500 can be consumed through the elastic supporting member 611, thereby being beneficial to inhibiting transmission of vibration, reducing noise generated by vibration, achieving the purpose of vibration reduction and noise reduction, improving the running performance of the rotor system 2000, and further improving the running stability of the fan 1000.
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 (10)
1. The fan, its characterized in that includes:
the shell is provided with a supporting frame, and the supporting frame is provided with a mounting hole;
the main shaft is rotationally arranged in the mounting hole;
the impeller is connected with the main shaft;
the bearing assembly comprises a shaft sleeve, the shaft sleeve is sleeved on the main shaft and is fixed in the mounting hole, the shaft sleeve and the main shaft are in clearance fit along the radial direction of the main shaft to form a gas bearing, an elastic supporting piece is arranged on the outer side wall of the shaft sleeve, the shaft sleeve is fixedly connected with the supporting frame through the elastic supporting piece, and the main shaft is rotationally arranged in the shaft sleeve;
the bearing assembly further comprises a first thrust disc and a second thrust disc, the first thrust disc and the second thrust disc are respectively positioned at two ends of the shaft sleeve along the axial direction and fixedly connected with the main shaft, and the first thrust disc and the second thrust disc are in clearance fit with the shaft sleeve along the axial direction; a plurality of second grooves are arranged between the first thrust disc and the shaft sleeve, and the second grooves are arranged on the end face of the first thrust disc at intervals along the circumferential direction of the main shaft; the second thrust disk is provided with a plurality of third grooves along the circumferential space on the end face of the second thrust disk, the inner diameter of the shaft sleeve is d1, the outer diameter of the shaft sleeve is d3, the positions of the second grooves along the radial minimum diameter is phi 1, the positions of the third grooves along the radial minimum diameter is phi 2, and the requirements are satisfied: d1+ (d 3-d 1)/2 < φ1=φ2 < 0.5mm+d1+ (d 3-d 1)/2.
2. The fan of claim 1, wherein the elastic support member is wrapped around the outer peripheral wall of the sleeve along the axial extension of the main shaft, and the elastic support member is located between the outer peripheral wall of the sleeve and the inner peripheral wall of the mounting hole.
3. The fan of claim 1 wherein the sleeve has a wall thickness d and the resilient support has a thickness k along a radial direction of the main shaft, the thickness being: k/d is more than or equal to 0.5 and less than or equal to 1.
4. The blower of claim 1, wherein the degree of stiffness of the resilient support is 40 degrees to 50 degrees.
5. The fan according to claim 1, wherein the main shaft comprises a shaft body and a shaft neck, the diameter of the shaft neck is larger than that of the shaft body, the shaft sleeve is sleeved on the shaft neck, a plurality of first grooves are formed in the outer peripheral wall of the shaft neck or the inner peripheral wall of the shaft sleeve, and the first grooves are arranged at intervals along the circumferential direction of the main shaft.
6. The fan of claim 5 wherein the sleeve has an inner diameter d1, the journal has a diameter d2, and the gap between the journal and the sleeve is f, satisfying: f= (d 1-d 2)/2 and 0.002mm < d1-d 2)/2 < 0.01mm.
7. The blower of claim 5, wherein the depths of the first, second, and third grooves are all h, satisfying: h is less than or equal to 0.005mm.
8. The fan of claim 5, wherein the first groove extends helically along the axial direction of the main shaft, and a first bending groove is connected to an end of the first groove along the axial direction of the main shaft away from the end surface of the journal.
9. The fan according to claim 1, wherein the second groove and the third groove extend spirally along the circumferential direction of the main shaft, the second groove is connected with a second bending groove along the radial direction of the main shaft at one end close to the axis of the main shaft, and the third groove is connected with a third bending groove along the radial direction of the main shaft at one end close to the axis of the main shaft.
10. Cleaning apparatus comprising a fan as claimed in any one of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210410028.7A CN114718890B (en) | 2022-04-19 | 2022-04-19 | Blower and cleaning device |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210410028.7A CN114718890B (en) | 2022-04-19 | 2022-04-19 | Blower and cleaning device |
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| CN114718890A CN114718890A (en) | 2022-07-08 |
| CN114718890B true CN114718890B (en) | 2023-12-22 |
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| CN114718890A (en) | 2022-07-08 |
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