CN117989231B - Double-row ball bearing and radiator fan - Google Patents
Double-row ball bearing and radiator fan Download PDFInfo
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- CN117989231B CN117989231B CN202410409526.9A CN202410409526A CN117989231B CN 117989231 B CN117989231 B CN 117989231B CN 202410409526 A CN202410409526 A CN 202410409526A CN 117989231 B CN117989231 B CN 117989231B
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- 238000005096 rolling process Methods 0.000 claims abstract description 93
- 125000006850 spacer group Chemical group 0.000 claims description 21
- 238000005457 optimization Methods 0.000 claims description 18
- 238000013461 design Methods 0.000 claims description 14
- 239000004519 grease Substances 0.000 claims description 13
- 238000002955 isolation Methods 0.000 claims description 13
- 238000007789 sealing Methods 0.000 claims description 12
- 238000009434 installation Methods 0.000 claims description 6
- 238000004458 analytical method Methods 0.000 claims description 2
- 238000001816 cooling Methods 0.000 abstract description 5
- 238000000034 method Methods 0.000 description 8
- 239000000314 lubricant Substances 0.000 description 3
- 239000010687 lubricating oil Substances 0.000 description 3
- 238000005260 corrosion Methods 0.000 description 2
- 230000007797 corrosion Effects 0.000 description 2
- 230000002028 premature Effects 0.000 description 2
- 230000002035 prolonged effect Effects 0.000 description 2
- 238000004088 simulation Methods 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 238000011900 installation process Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
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Abstract
The application provides a double-row ball bearing and a cooling fan. The double-row ball bearing includes: an inner race having an outer surface comprising a flat circumferential outer annulus and a recessed first raceway; an outer race having an inner surface comprising a flat circumferential inner annulus and a recessed second raceway; the retainer, its axial both sides are used for holding first row rolling element and second row rolling element respectively, first row rolling element is limited in between first raceway and the second raceway, second row rolling element is limited in between the circumference outer ring face and the circumference inner ring face, first row rolling element includes a plurality of first balls, second row rolling element includes a plurality of second balls, the diameter of first ball is greater than the diameter of second ball. The double-row ball bearing provided by the application has the advantages that the assembly efficiency is obviously improved, and the assembly complexity is reduced.
Description
Technical Field
The application relates to the technical field of bearings, in particular to a double-row ball bearing and a cooling fan.
Background
In the bearing design of the radiator fan, radial loads caused by the fan blades, i.e., loads perpendicular to the axial direction, are mainly considered. The centrifugal force generated by the blades due to the rotation of the fan makes the bearing need to effectively bear radial load, and relatively small axial load has less influence on the bearing.
Since the bearing is mainly subjected to radial load in the radiator fan, angular contact bearings are not generally used, but deep groove ball bearings are used. To meet the high rotational speed requirement, the cooling fan typically selects a double row deep groove ball bearing. This bearing design has excellent radial bearing capacity, ensuring stable operation under high speed rotation and high radial load operating conditions. The double-row deep groove ball bearing provides excellent bearing capacity, and effectively reduces radial stress of the bearing in an extreme working environment. In addition, the double-row deep groove ball bearing not only has excellent vibration resistance and stability, but also has longer service life. This not only helps to reduce the maintenance requirements of the equipment, but also prolongs the replacement cycle, improving the reliability and stability of the overall system.
Double-row deep groove ball bearings typically employ two rows of rolling bodies of similar or comparable diameters. With this design, when the bearing is subjected to radial loads, the two rows of rolling bodies share the load in a similar manner, helping to achieve a uniform load distribution inside the bearing, which helps to improve the life, stability and performance of the bearing. Therefore, a double-row deep groove ball bearing with rolling bodies having similar diameters or small differences is generally selected for the heat dissipation fan.
When the double-row deep groove ball bearing is assembled, the first row of rolling bodies can be assembled by tilting the retainer, but after the first row of rolling bodies are assembled, the retainer is positioned so that the retainer cannot tilt to form an attitude easy to assemble the rolling bodies, and therefore, the second row of rolling bodies has the problem of difficult assembly. In the face of the problem of difficult assembly of double-row deep groove ball bearings, technicians typically use special guiding tools and jigs to ensure the correct position of the bearings during assembly, but this approach results in reduced assembly efficiency and more complex assembly of double-row deep groove ball bearings.
Disclosure of Invention
An object of the present invention is to provide a new structure form which is significantly different from the existing double-row deep groove ball bearing, so as to improve the assembly efficiency and reduce the assembly complexity.
In particular, the application proposes a double-row ball bearing comprising:
an inner race having an outer surface comprising a flat circumferential outer annulus and a recessed first raceway;
An outer race having an inner surface comprising a flat circumferential inner annulus and a recessed second raceway;
The retainer, its axial both sides are used for holding first row rolling element and second row rolling element respectively, first row rolling element is limited in between first raceway and the second raceway, second row rolling element is limited in between the circumference outer ring face and the circumference inner ring face, first row rolling element includes a plurality of first balls, second row rolling element includes a plurality of second balls, the diameter of first ball is greater than the diameter of second ball.
Optionally, the number of second balls is greater than the number of first balls.
Optionally, the double-row ball bearing further comprises:
The annular isolation frame is arranged between the inner ring and the outer ring and is positioned at one end of the second row of rolling bodies, which is far away from the first row of rolling bodies, one side of the isolation frame is used for limiting the second row of rolling bodies, a sealing installation groove and a containing groove are arranged at the inner surface of the isolation frame facing the inner ring, the sealing installation groove is positioned between the second row of rolling bodies and the containing groove in the axial direction, the sealing installation groove is used for installing an isolation sealing ring, and the containing groove is used for containing conductive grease.
Optionally, a preset gap is formed between the isolation frame and the inner ring.
Optionally, a third raceway matched with the second row of rolling bodies is arranged on one side of the isolation frame facing the second row of rolling bodies.
Optionally, the retainer is equipped with a plurality of first ball grooves in axial one side, and the opposite side is equipped with a plurality of second ball grooves, first ball groove is used for the joint first ball, the second ball groove is used for the joint second ball.
Optionally, the diameter of the first balls, the number of the second balls, the thickness of the cage, and the depth of the third raceway are determined according to a target contact stress.
Optionally, the target contact stress includes a first threshold value and a second threshold value, the first maximum contact stress of the first row of rolling elements and the second maximum contact stress of the second row of rolling elements of the double row ball bearing under the target load are calculated through a finite element analysis method, wherein design variables include the diameter of the first balls, the number of the second balls, the thickness of the cage and the depth of the third rollaway nest are design variables, and an optimization target includes that the maximum value of the first maximum contact stress and the second maximum contact stress is smaller than the first threshold value, and the difference value of the first maximum contact stress and the second maximum contact stress is smaller than the second threshold value.
In particular, the invention also provides a cooling fan comprising a motor, wherein the motor comprises the double-row ball bearing.
According to a first aspect of the application, the first row of rolling elements is radially associated with the first raceway and the second raceway, respectively, i.e. the conventional ball assembly is maintained, and the second row of rolling elements is radially associated directly with the circumferential outer annular surface of the inner ring and the circumferential inner annular surface of the outer ring, i.e. the second row of rolling elements is no longer provided with corresponding raceways, thereby innovatively providing a new construction which is significantly different from the existing double-row deep groove ball bearing. Because the second row of rolling bodies do not have rollaway nest, the installation process of the double-row ball bearing is not additionally hindered, and each second ball can be conveniently assembled to the retainer after all the first balls are assembled without being limited by the inner ring and the outer ring, so that the assembly efficiency is obviously improved, and the assembly complexity is reduced.
Further, since the second row of rolling bodies does not have a raceway, it is inevitable that the diameter of the first ball is larger than that of the second ball, and the first ball and the second ball may be arranged offset in the axial direction, so that the width of the bearing may be compressed, allowing the double row ball bearing to be used with a limited axial size.
According to the second aspect of the invention, the double-row ball bearing is provided with the spacer frame on one side of the second row rolling bodies, one side of the spacer frame is used for limiting the second row rolling bodies to play a role in assisting in limiting the second row rolling bodies, meanwhile, the spacer frame is also used for installing the spacer seal ring and containing conductive grease, and shaft voltage between the inner ring and the outer ring of the double-row ball bearing can be released through the conductive grease and the spacer frame, so that the electric corrosion of the double-row ball bearing is reduced, the service life of the bearing is prolonged, and the arrangement of the spacer seal ring also plays a role in insulating the lubricating oil and the conductive grease while sealing the lubricating oil.
Further, through limiting the clearance between isolation frame and the inner circle and the distance between one side of isolation frame near the holding groove and the holding groove, guaranteed sealed clearance and seal length, can effectively prevent that conductive grease from spilling over, and then no longer need set up the seal structure who is used for sealed conductive grease specially, simplified the structure.
According to the third aspect of the invention, the spacer is further provided with the third rollaway nest matched with the second row of rolling bodies, so that the contact area between each second ball of the second row of rolling bodies and other parts can be increased, stress is dispersed, contact stress at the positions of the second ball, the inner ring and the outer ring can be reduced, and the service life of the bearing is prolonged.
According to the fourth aspect of the invention, the diameter of the first balls, the number of the second balls, the thickness of the retainer and the depth of the third ball track are determined according to the target contact stress, wherein the target contact stress comprises a first threshold value and a second threshold value, namely, the maximum value of the first maximum contact stress and the second maximum contact stress is smaller than the first threshold value, and the difference value of the first maximum contact stress and the second maximum contact stress is smaller than the second threshold value as an optimization target, so that the maximum contact stress of the double-row ball bearing can be ensured to meet the requirement, the difference value of the maximum contact stress of two sides is ensured not to be too large after the ball diameter of one side is changed, premature abrasion caused by overlarge maximum contact stress of the balls of the one side is avoided, the stress of the two sides of the optimized double-row ball bearing is more balanced, and the service life of the double-row ball bearing is further improved.
Further, since the diameter of the first balls, the number of the second balls, the thickness of the cage and the depth of the third raceway are parameters that directly affect the contact area, when the optimization design is performed, the contact stress can be effectively adjusted by changing the parameters, so that the optimization process is more efficient and reasonable.
Drawings
FIG. 1 shows a schematic exploded view of a double row ball bearing according to one embodiment of the invention;
FIG. 2 shows a schematic cross-sectional view of a part of the structure of a double row ball bearing according to one embodiment of the invention;
FIG. 3 shows a schematic cross-sectional view of a double row ball bearing according to another embodiment of the invention;
fig. 4 shows a schematic cross-sectional view of a double row ball bearing according to a further embodiment of the invention;
fig. 5 shows a schematic structural view of a cage of a double row ball bearing according to an embodiment of the present invention.
Detailed Description
In order that the above objects, features and advantages of the application will be readily understood, a more particular description of the application will be rendered by reference to the appended drawings. It is to be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the scope of the application. It should be further noted that, for convenience of description, only some, but not all of the structures related to the present application are shown in the drawings. All other embodiments, which can be made by those skilled in the art based on the embodiments of the application without making any inventive effort, are intended to be within the scope of the application.
The terms "comprising" and "having" and any variations thereof herein are intended to cover a non-exclusive inclusion. For example, a process, method, system, article, or apparatus that comprises a list of steps is not limited to the elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus.
Reference herein to "an embodiment" means that a particular feature, structure, or characteristic described in connection with the embodiment may be included in at least one embodiment of the application. The appearances of such phrases in various places in the specification are not necessarily all referring to the same embodiment, nor are separate or alternative embodiments mutually exclusive of other embodiments. Those of skill in the art will explicitly and implicitly appreciate that the embodiments described herein may be combined with other embodiments.
Fig. 1 shows a schematic exploded structure of a double row ball bearing according to an embodiment of the present application. Fig. 2 shows a schematic cross-sectional view of a part of the structure of a double row ball bearing according to an embodiment of the application, with the first end cap 81, the first seal ring 71, the second end cap 82 and the second seal ring 72 omitted in fig. 2. The inventor of the present application innovatively proposes a new structural form that is significantly different from the existing double-row ball bearing. As shown in fig. 1, in one embodiment, the double row ball bearing includes an inner race 10, an outer race 20, a cage 30, a first row of rolling elements 40, and a second row of rolling elements 50. The outer surface of the inner ring 10 comprises a flat circumferential outer annulus 11 and a recessed first raceway 12. The inner surface of the outer race 20 includes a flat circumferential inner annulus 21 and a recessed second raceway 22. The cage 30 has both axial sides for holding the first row of rolling elements 40 and the second row of rolling elements 50, respectively. As shown in fig. 2, the first row of rolling elements 40 is confined between the first raceway 12 and the second raceway 22, the second row of rolling elements 50 is confined between the circumferential outer ring surface 11 and the circumferential inner ring surface 21, the first row of rolling elements 40 includes a plurality of first balls 41, and the second row of rolling elements 50 includes a plurality of second balls 51, and the diameter of the first balls 41 is larger than the diameter of the second balls 51. Of course, generally, as shown in fig. 1, a first end cover 81 and a first seal ring 71 are further disposed on a side of the first row of rolling elements 40 away from the second row of rolling elements 50 in order, and a second end cover 82 and a second seal ring 72 are further disposed on a side of the second row of rolling elements 50 away from the first row of rolling elements 40 in order to seal lubricating oil.
In the present embodiment, the first row of rolling elements 40 is radially engaged with the first raceway 12 and the second raceway 22, respectively, i.e. the conventional ball assembly is maintained, and the second row of rolling elements 50 is radially engaged with the circumferential outer ring surface 11 of the inner ring 10 and the circumferential inner ring surface 21 of the outer ring 20, i.e. the second row of rolling elements 50 is no longer provided with corresponding raceways, thereby innovatively providing a new structure that is significantly different from the existing double-row deep groove ball bearing. Since the second row rolling elements 50 do not have raceways, the mounting process of the double row ball bearing of the present application is not additionally hindered, and each second ball 51 can be conveniently mounted to the cage 30 after all the first balls 41 are mounted, without being limited by the inner ring 10 and the outer ring 20, thereby remarkably improving the mounting efficiency and reducing the mounting complexity.
Further, since the second row of rolling elements 50 does not have a raceway, it is inevitable that the diameter of the first ball 41 is larger than that of the second ball 51, and the first ball 41 and the second ball 51 may be arranged offset in the axial direction, so that the width of the bearing can be compressed, allowing the double row ball bearing to be used with a limited axial size.
In one embodiment, the number of second balls 51 is larger than the number of first balls 41, and since the diameter of the second balls 51 is smaller than the diameter of the first balls 41 and there is no corresponding raceway for the second balls 51, the contact stress to which the second balls 51 are subjected is larger than that of the first balls 41, so that the total contact area of the second row of rolling elements 50 can be increased by increasing the number of second balls 51, which is advantageous in reducing the contact stress distributed to each second ball 51 and in balancing the stress of the first row of rolling elements 40 and the second row of rolling elements 50.
Fig. 3 shows a schematic cross-sectional view of a double row ball bearing according to another embodiment of the invention. As shown in fig. 3, in another embodiment, the double-row ball bearing further includes an annular spacer 60 disposed between the inner ring 10 and the outer ring 20 and located at an end of the second row of rolling elements 50 away from the first row of rolling elements 40, one side of the spacer 60 is used for limiting the second row of rolling elements 50, a seal mounting groove 61 and a receiving groove 62 are provided at an inner surface of the spacer 60 facing the inner ring 10, the seal mounting groove 61 is located between the second row of rolling elements 50 and the receiving groove 62 in an axial direction, the seal mounting groove 61 is used for mounting the seal ring 70, and the receiving groove 62 is used for placing conductive grease.
Since the second balls 51 of the second row of rolling elements 50 in the double row ball bearing in the present embodiment have no raceways on the inner ring 10 and the outer ring 20, the positioning stability of the rolling elements of the second row is slightly inferior to that of the rolling elements of the first row 40, which puts a higher demand on the stopper capability of the cage 30. On this basis, the double-row ball bearing of the present embodiment is provided with the spacer 60 on one side of the second row rolling elements 50, and this spacer 60 is provided on one side for restricting the second row rolling elements 50 to function as an auxiliary restriction of the second row rolling elements 50, and this spacer 60 is also provided for mounting the spacer seal ring 70 and accommodating the conductive grease, and the shaft voltage between the inner ring 10 and the outer ring 20 of the double-row ball bearing can be released through the conductive grease and the spacer 60, thereby reducing the electric corrosion of the double-row ball bearing and improving the bearing life, wherein the lubricant provided in the part space of the spacer seal ring 70 between the seal lubricant (the inner ring 10 and the outer ring 20 for placing the retainer 30) is used for lubricating the first row rolling elements 40 and the second row rolling elements 50) while also functioning as a spacer lubricant and conductive grease.
In a further embodiment, the spacer 60 has a predetermined gap d with the inner ring 10. Here, the side of the spacer 60 away from the second row rolling elements 50 does not exceed the end face of the inner ring 10 at the end close to the second row rolling elements 50. The preset gap d may take any value from 0.03 to 0.07mm, for example 0.03mm, 0.05mm or 0.07mm.
In this embodiment, the gap between the isolation frame 60 and the inner ring 10 is limited to ensure a sealing gap, so that the conductive grease can be effectively prevented from overflowing, and a sealing structure special for sealing the conductive grease is not required, thereby simplifying the structure.
Fig. 4 shows a schematic cross-sectional view of a double row ball bearing according to a further embodiment of the invention. As shown in fig. 4, in one embodiment, the side of the cage 60 facing the second row of rolling elements 50 is provided with a third raceway 63 that mates with the second row of rolling elements 50.
In the foregoing embodiment, the raceways on the inner ring 10 and the outer ring 20 are eliminated for the convenience of assembling the second row of rolling bodies 50, so that the diameters of the respective second balls 51 of the second row of rolling bodies 50 are reduced and the contact areas with the inner ring 10 and the outer ring 20 are also reduced, and thus the contact stress of the second balls 51 is increased. On this basis, the spacer 60 of the present embodiment is further provided with a third raceway 63 matching with the second row of rolling elements 50, so that the contact area between each second ball 51 of the second row of rolling elements 50 and other components can be increased, the stress can be dispersed more, and the contact stress at the positions of the second ball 51, the inner ring 10 and the outer ring 20 can be reduced, which is beneficial to improving the bearing life.
Fig. 5 shows a schematic structural view of a cage 30 of a double row ball bearing according to an embodiment of the present invention. As shown in fig. 5, in one embodiment, the cage 30 is provided with a plurality of first ball grooves 31 on one side in the axial direction, and a plurality of second ball grooves 32 on the other side, wherein the first ball grooves 31 are used for clamping the first balls 41, and the second ball grooves 32 are used for clamping the second balls 51. The openings of the first ball groove 31 and the second ball groove 32 are required to be sized so that the corresponding first ball 41 and second ball 51 are not separated, and to facilitate the assembly of the first ball 41 and second ball 51.
In one embodiment, the diameter of the first balls 41, the number of the second balls 51, the thickness of the cage 30, and the depth of the third raceway 63 are determined according to the target contact stress. I.e. the diameter of the first balls 41, the number of the second balls 51, the thickness of the cage 30 and the depth of the third raceway 63 are determined with the target contact stress as an optimization target. The specific optimization mode may be to establish a fitting formula, and then determine each parameter of the fitting formula through experimental or simulation data, or perform optimization design on each parameter by using an existing optimization simulation tool, for example, common ansys finite element analysis software.
In one embodiment, the ansys finite element analysis software is selected for optimization, and the specific optimization process generally includes modeling, meshing, loading, material performance parameter input, design variable input, boundary condition setting, and optimization objective setting, which are conventional optimization steps not described in detail herein. In the present embodiment, taking the maximum value of the first maximum contact stress and the second maximum contact stress being smaller than the first threshold value and the difference between the first maximum contact stress and the second maximum contact stress being smaller than the second threshold value as the optimization target, the design variables include the diameter of the first balls 41, the number of the second balls 51, the thickness of the cage 30, and the depth of the third raceway 63, and the ranges of the respective design variables are set, for example, the range of the diameter of the first balls 41 may be determined by increasing the distance between the inner ring 10 and the outer ring 20 by a certain value, the range of the number of the second balls 51 may be determined by the diameter of the second balls 51 and the outer diameter of the cage 30, the range of the thickness of the cage 30 may be determined by the diameter of the second balls 51, and the range of the depth of the third raceway 63 may be set by the size of the portion of the second balls 51 exposed to the second ball groove 32. And then applying a certain radial load, and performing finite element operation by using a common contact theory, such as Hertz contact theory, so as to obtain a first maximum contact stress of the first row of rolling elements 40 and a second maximum contact stress of the second row of rolling elements 50 of the double-row ball bearing under the target load, and obtaining an optimized value of a design variable conforming to the optimized target according to the optimized target, wherein the optimized value is the final parameter of the double-row ball bearing. Of course, the above-mentioned optimization objectives may not be met at the same time, and if only one item can be met, the maximum value of the first maximum contact stress and the second maximum contact stress is preferably met to be smaller than the first threshold value.
In this embodiment, the diameter of the first balls 41, the number of the second balls 51, the thickness of the cage 30 and the depth of the third raceway 63 are determined according to the target contact stress, where the target contact stress includes a first threshold and a second threshold, that is, the maximum value of the first maximum contact stress and the second maximum contact stress is smaller than the first threshold, and the difference between the first maximum contact stress and the second maximum contact stress is smaller than the second threshold as an optimization target, so that the maximum contact stress of the double-row ball bearing can be ensured to meet the requirement, and the difference between the maximum contact stress of two sides is ensured not to be too large after the ball diameter of one side is changed, so that premature wear caused by overlarge maximum contact stress of the balls of one side is avoided, and the stress of two sides of the optimized double-row ball bearing is more balanced, thereby further improving the bearing life.
Since the diameter of the first balls 41, the number of the second balls 51, the thickness of the cage 30, and the depth of the third raceway 63 are parameters that directly affect the contact area, the above-described parameter changes can effectively adjust the contact stress when the optimization design is performed, so that the optimization process is more efficient and reasonable.
An embodiment of the present invention further provides a cooling fan, including a motor, where the motor includes the double-row ball bearing in any one of the above embodiments.
The foregoing is merely exemplary of some embodiments of the application and other modifications may be made without departing from the spirit of the application.
Claims (9)
1. A double row ball bearing comprising:
an inner race having an outer surface comprising a flat circumferential outer annulus and a recessed first raceway;
An outer race having an inner surface comprising a flat circumferential inner annulus and a recessed second raceway;
The retainer, its axial both sides are used for holding first row rolling element and second row rolling element respectively, first row rolling element is limited in between first raceway and the second raceway, second row rolling element is limited in between the circumference outer ring face and the circumference inner ring face, first row rolling element includes a plurality of first balls, second row rolling element includes a plurality of second balls, the diameter of first ball is greater than the diameter of second ball.
2. The double row ball bearing of claim 1 wherein the number of second balls is greater than the number of first balls.
3. The double row ball bearing of claim 1, further comprising:
The annular isolation frame is arranged between the inner ring and the outer ring and is positioned at one end of the second row of rolling bodies, which is far away from the first row of rolling bodies, one side of the isolation frame is used for limiting the second row of rolling bodies, a sealing installation groove and a containing groove are arranged at the inner surface of the isolation frame facing the inner ring, the sealing installation groove is positioned between the second row of rolling bodies and the containing groove in the axial direction, the sealing installation groove is used for installing an isolation sealing ring, and the containing groove is used for containing conductive grease.
4. A double row ball bearing according to claim 3, wherein the spacer and the inner ring have a predetermined gap therebetween.
5. A double row ball bearing according to claim 3, wherein the side of the cage facing the second row of rolling elements is provided with a third raceway matching the second row of rolling elements.
6. The double-row ball bearing according to claim 1, wherein the retainer is provided with a plurality of first ball grooves on one side in the axial direction and a plurality of second ball grooves on the other side, the first ball grooves being for engaging the first balls, and the second ball grooves being for engaging the second balls.
7. The double row ball bearing of claim 5 wherein the diameter of the first balls, the number of second balls, the thickness of the cage, and the depth of the third raceway are determined according to a target contact stress.
8. The double row ball bearing of claim 7, wherein the target contact stress comprises a first threshold and a second threshold, and wherein the first maximum contact stress of the first row of rolling elements and the second maximum contact stress of the second row of rolling elements under the target load are calculated by a finite element analysis method, wherein design variables comprise a diameter of the first balls, a number of the second balls, a thickness of the cage, and a depth of the third raceway as design variables, and wherein an optimization objective comprises a maximum of the first maximum contact stress and the second maximum contact stress being less than the first threshold, and a difference of the first maximum contact stress and the second maximum contact stress being less than the second threshold.
9. A radiator fan comprising a motor including the double row ball bearing as claimed in any one of claims 1 to 8.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202410409526.9A CN117989231B (en) | 2024-04-07 | 2024-04-07 | Double-row ball bearing and radiator fan |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202410409526.9A CN117989231B (en) | 2024-04-07 | 2024-04-07 | Double-row ball bearing and radiator fan |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN117989231A CN117989231A (en) | 2024-05-07 |
| CN117989231B true CN117989231B (en) | 2024-06-11 |
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| CN202410409526.9A Active CN117989231B (en) | 2024-04-07 | 2024-04-07 | Double-row ball bearing and radiator fan |
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|---|---|---|---|---|
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| JP2012102781A (en) * | 2010-11-09 | 2012-05-31 | Nsk Ltd | Tandem angular contact ball bearing |
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| CN107747594A (en) * | 2017-04-19 | 2018-03-02 | 山东吉恩纳机械工程技术有限公司 | A kind of robot biserial thin-walled seal ball bearing |
| CN207470609U (en) * | 2017-11-29 | 2018-06-08 | 河北万转腾远轴承有限公司 | A kind of double deep groove ball bearing |
| CN113847336A (en) * | 2021-08-16 | 2021-12-28 | 人本股份有限公司 | Hub bearing |
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| CN117989231A (en) | 2024-05-07 |
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