Permanent magnet auxiliary load assisted two-stage tandem bearing outer layer rotation method

Abstract

The application discloses a permanent magnet auxiliary load assisted double-stage tandem bearing outer layer rotating method and relates to the field of bearing transmission analysis. The method comprises the following steps: setting structure parameters of a double-stage tandem rolling bearing, combining with a magnetic adsorption load, and calculating friction torques of inner ring rolling bodies and outer ring rolling bodies of the double-stage tandem rolling bearing; calculating friction torques generated by driving force of the double-stage tandem rolling bearing on the inner ring rolling bodies and the outer ring rolling bodies, and outputting the driving force of the double-stage tandem rolling bearing; solving the driving force of the double-stage tandem rolling bearing and the friction torque equation of the inner ring rolling bodies and the outer ring rolling bodies, and obtaining a driving force overcoming friction torque relationship formula of the double-stage tandem rolling bearing; and reasonably dividing the structure of the double-stage tandem rolling bearing, so that the outer layer bearing can realize stable rotation under the conditions of starting and light load, the rotating performance of the outer layer bearing is effectively improved, and the method has a good popularization and application prospect.

Description

Technical Field

[0001] This invention relates to the field of bearing transmission analysis technology, and in particular to a method for using permanent magnet additional load to assist the rotation of the outer layer of a two-stage series bearing. Background Technology

[0002] In a rolling bearing assembly employing a two-stage tandem structure, the bearing system typically consists of an inner bearing, an outer bearing, and a connecting structure positioned between them. This structure allows the inner and outer bearings to form a series connection to meet specific installation or operational requirements. The rotational state of the outer bearing usually depends on the transmission action of the inner bearing and the connecting structure. The contact state between the rolling elements and the raceway has a significant impact on the operational stability of the outer bearing. Especially in a two-stage tandem bearing structure that includes intermediate components such as a connecting ring, the force path of the outer bearing is relatively independent, and the effective load of the rolling elements mainly comes from internal contact transmission. When the system is in the startup or load change phase, the contact state between the rolling elements and the raceway of the outer bearing is more prone to fluctuation, which in turn leads to a decrease in the rotational stability of the outer bearing.

[0003] Existing technologies typically improve the situation by adjusting assembly preload, changing structural dimensions, or optimizing lubrication conditions. These methods largely rely on mechanical structures, have limited adjustment ranges, and may introduce additional friction or increase assembly complexity under certain operating conditions. Research on the rotation problem of the outer bearing in a two-stage tandem rolling bearing has focused on optimizing structural parameters or assembly methods. Research on techniques for applying additional loads to the rolling elements of the outer bearing in a non-contact manner to control the stress state and contact behavior remains relatively limited. Summary of the Invention

[0004] In view of the aforementioned existing problems, the present invention is proposed.

[0005] Therefore, this invention provides a method for assisting the rotation of the outer layer of a two-stage tandem rolling bearing with a permanent magnet additional load to solve the problem of unstable rotation caused by the outer layer bearing's reliance on passive friction transmission and the difficulty in controlling the load state.

[0006] To solve the above-mentioned technical problems, the present invention provides the following technical solution:

[0007] This invention provides a method for assisting the outer rotation of a two-stage tandem bearing with a permanent magnet additional load. The method includes: dividing the two-stage tandem rolling bearing into two parts: the bearing body and a permanent magnet loading system, with the core of the permanent magnet loading system being a permanent magnet unit; calculating the magnetic adsorption load applied to the outer auxiliary bearing balls by the permanent magnet based on the magnetic field distribution formed by the permanent magnet unit in the bearing air gap; setting various structural parameters of the two-stage tandem rolling bearing and calculating the frictional torque of the inner and outer rolling elements of the two-stage tandem rolling bearing in conjunction with the magnetic adsorption load; calculating the frictional torque generated by the driving force of the two-stage tandem rolling bearing on the inner and outer rolling elements, and outputting the driving force of the two-stage tandem rolling bearing; comparing and analyzing the driving force of the two-stage tandem rolling bearing with the frictional torque of the inner and outer rolling elements according to the mechanical principles of rolling bearings, and outputting the conditions for determining the rotation of the outer bearing; and solving the equations for the driving force of the two-stage tandem rolling bearing and the frictional torque of the inner and outer rolling elements to obtain the relationship between the driving force of the two-stage tandem rolling bearing and the frictional torque.

[0008] As a preferred embodiment of the permanent magnet additional load assisted rotation of the outer layer of the double-stage series bearing described in this invention, the bearing body is composed of an inner main bearing and an outer auxiliary bearing connected in series, and the permanent magnet loading system is embedded in the transition ring between the double-stage series rolling bearings.

[0009] As a preferred embodiment of the method for assisting the rotation of the outer layer of a two-stage tandem bearing with a permanent magnet additional load according to the present invention, wherein: the expression for calculating the magnetic adsorption load applied by the permanent magnet to the outer auxiliary bearing balls is:

[0010] ;

[0011] in, This represents the equivalent magnetic attraction force of a permanent magnet. Indicates the number of permanent magnets. Indicates the magnetic force utilization coefficient. This represents the air gap magnetic flux density. It represents the vacuum permeability.

[0012] As a preferred embodiment of the permanent magnet additional load assisted rotation method for the outer layer of a two-stage tandem bearing according to the present invention, the structural parameters of the two-stage tandem rolling bearing include: driving power. Input speed Inner ring bearing speed Outer ring bearing speed Pitch circle diameter of inner ring bearing outer ring bearing pitch circle diameter Inner ring bearing normal load The original normal phase load of the outer ring bearing Kinematic viscosity of inner ring bearing lubricating oil Kinematic viscosity of outer ring bearing lubricating oil Lubricating viscosity coefficient Load-related friction coefficient Number of permanent magnets Magnetic utilization coefficient air gap magnetic flux density Vacuum permeability Effective area Equivalent magnetic attraction force Torque of the inner ring bearing independent of load Torque of the outer ring bearing independent of load Torque related to load in inner ring bearing Torque related to load in outer ring bearings and driving force .

[0013] As a preferred embodiment of the method for assisting the outer rotation of a two-stage tandem bearing with a permanent magnet additional load according to the present invention, wherein: the expression for calculating the torque of the inner ring rolling element of the two-stage tandem rolling bearing independent of the load is:

[0014] when When ≥2000, ;

[0015] when <2000, .

[0016] As a preferred embodiment of the method for assisting the outer rotation of a two-stage tandem bearing with a permanent magnet additional load as described in this invention, the expression for calculating the torque of the outer rolling element of the two-stage tandem rolling bearing independent of the load is as follows:

[0017] when When ≥2000, ;

[0018] when <2000, .

[0019] As a preferred embodiment of the method for assisting the outer rotation of a two-stage tandem bearing with a permanent magnet additional load as described in this invention, wherein: the calculation of the torque related to the load on the inner ring rolling element of the two-stage tandem rolling bearing is described. The expression is:

[0020] ;

[0021] Calculate the torque of the outer ring rolling elements of a two-stage tandem rolling bearing in relation to the load. The expression is:

[0022] .

[0023] As a preferred embodiment of the permanent magnet additional load assisted rotation of the outer layer of a two-stage tandem bearing according to the present invention, wherein: the calculation of the driving force of the two-stage tandem rolling bearing... The expression is:

[0024] .

[0025] As a preferred embodiment of the permanent magnet additional load assisted rotation of the outer layer of the two-stage tandem bearing described in this invention, the relationship between the driving force and the frictional torque of the two-stage tandem rolling bearing is:

[0026] .

[0027] The beneficial effects of this invention are as follows: By rationally dividing the structure of the double-stage tandem rolling bearing, establishing a relationship model between the driving force and frictional torque of the outer bearing, analyzing and determining whether the outer bearing has the conditions for rotation, and based on fully considering the original mechanical characteristics of the bearing, applying auxiliary loads to the rolling elements of the outer bearing through a non-contact magnetic loading method, the outer bearing can achieve stable rotation under starting and light load conditions, thus effectively improving the rotational performance of the outer bearing. This provides a new technical approach and engineering reference for the design and application of double-stage tandem rolling bearings under complex working conditions, and has good prospects for promotion and application. Attached Figure Description

[0028] To more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings used in the following description of the embodiments will be briefly introduced. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0029] Figure 1 A flowchart of a method for applying an additional load to a permanent magnet to assist the rotation of the outer layer of a two-stage tandem bearing.

[0030] Figure 2 This is a schematic diagram of a two-stage tandem rolling bearing.

[0031] Figure 3 This is a front view of a two-stage tandem rolling bearing.

[0032] Figure 4 This is a schematic diagram of the first-stage bearing.

[0033] Figure 5 This is a schematic diagram of the entire secondary bearing.

[0034] Figure 6 This is a schematic diagram of the adapter ring as a whole.

[0035] In the diagram: 1. Primary bearing; 2. Secondary bearing; 3. Adapter ring; 11. Primary ball bearing; 12. Inner ring of primary bearing; 13. Outer ring of primary bearing; 14. Cage of primary bearing; 21. Inner ring of secondary bearing; 22. Outer ring of secondary bearing; 23. Outer ring of secondary bearing; 24. Cage of secondary bearing; 31. Permanent magnet. Detailed Implementation

[0036] To make the above-mentioned objects, features and advantages of the present invention more apparent and understandable, the specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings.

[0037] Many specific details are set forth in the following description in order to provide a full understanding of the invention. However, the invention may also be practiced in other ways different from those described herein, and those skilled in the art can make similar extensions without departing from the spirit of the invention. Therefore, the invention is not limited to the specific embodiments disclosed below.

[0038] Secondly, the term "one embodiment" or "embodiment" as used herein refers to a specific feature, structure, or characteristic that may be included in at least one implementation of the present invention. The phrase "in one embodiment" appearing in different places in this specification does not necessarily refer to the same embodiment, nor is it a single or selective embodiment that is mutually exclusive with other embodiments.

[0039] Reference Figures 1-6 As one embodiment of the present invention, this embodiment provides a method for rotating the outer layer of a two-stage tandem bearing with a permanent magnet additional load, comprising the following steps:

[0040] S1. The two-stage tandem rolling bearing is divided into two parts: the bearing body and the permanent magnet loading system. The core of the permanent magnet loading system is the permanent magnet unit.

[0041] The bearing body consists of an inner main bearing and an outer auxiliary bearing connected in series, with a permanent magnet loading system embedded in the transition ring between the two-stage series rolling bearings.

[0042] Specifically, the double-stage tandem rolling bearing mainly consists of an inner first-stage bearing 1 and an outer second-stage bearing 2. The first-stage bearing 1 is located in the innermost layer of the entire bearing structure and adopts a ball bearing design, including a first-stage ball 11, a first-stage bearing inner ring 12, a first-stage bearing outer ring 13, and a first-stage bearing cage 14. The primary ball bearing 11 rolls within the raceway formed by the inner ring 12 and outer ring 13 of the primary bearing, achieving rotation and support functions. The secondary bearing 2, located at the outermost layer of the entire bearing structure, is also a ball bearing design, similar to the primary bearing, and includes the secondary bearing inner ring 21, secondary ball bearing 22, secondary bearing outer ring 23, and secondary bearing cage 24. The transition ring 3 is located between the primary and secondary bearings, serving as an intermediate connecting component of the two-stage tandem rolling bearing. Its inner side mates with the outer ring of the primary bearing, and its outer side connects to the inner ring of the secondary bearing. The transition ring 3 is equipped with a magnetic loading structure for mounting permanent magnets, including the transition ring body 3 and a permanent magnet 31 set in the permanent magnet mounting groove, for applying magnetic adsorption load to the secondary bearing balls. The bearing body and the permanent magnet loading system are respectively the bearing body composed of the primary and secondary bearings, and the permanent magnet loading system composed of the transition ring and the permanent magnet.

[0043] The core of the permanent magnet loading system consists of permanent magnet units distributed in a Heilbeck array. The magnetic field generated by the permanent magnet units applies a controllable additional load to the balls of the outer auxiliary bearing.

[0044] Specifically, Figure 6 This is an overall schematic diagram of the adapter ring of the present invention. The adapter ring 3 is disposed between the primary bearing 1 and the secondary bearing 2. Its inner side is engaged with the outer ring 13 of the primary bearing, and its outer side is adjacent to the inner ring 22 of the secondary bearing. Multiple permanent magnet mounting structures are provided on the adapter ring 3 along the circumferential direction for mounting permanent magnets 31. The permanent magnets 31 are arranged in a Hellbeck array, so that the adapter ring 3 forms an enhanced magnetic field distribution on the side close to the secondary bearing.

[0045] During the start-up phase or under light load conditions, the mechanical load on the outer bearing is relatively small, and the contact force between the balls and the raceway is insufficient, which can easily lead to difficulty in starting the outer bearing or unstable rotation. By applying magnetic adsorption load through the permanent magnet 31 on the adapter ring 3, additional radial or axial load compensation can be provided for the balls of the secondary bearing without increasing the mechanical contact structure, thereby effectively improving the fit between the balls and the raceway and reducing the risk of uneven friction and local slippage during the start-up of the outer bearing.

[0046] It should also be noted that by setting a permanent magnet structure on the transition ring between the primary and secondary bearings, the transition ring has the dual function of structural connection and magnetic load carrier. The permanent magnets are preferably arranged in a Halebeck array, so that the magnetic field is enhanced on the side closer to the outer bearing, thereby applying a controllable magnetic adsorption load to the outer bearing balls. Without adding an additional mechanical contact structure, the stress state between the balls and the raceway is improved, the starting resistance of the outer bearing is reduced, and the running stability is improved.

[0047] S2. Based on the magnetic field distribution formed by the permanent magnet unit in the bearing air gap, calculate the magnetic adsorption load applied by the permanent magnet to the outer auxiliary bearing balls;

[0048] Specifically, based on the magnetic field distribution formed by the permanent magnet unit in the bearing air gap, combined with the geometric dimensions, magnetization direction and arrangement of the permanent magnet unit on the transition ring, the magnetic circuit relationship between the permanent magnet and the bearing air gap is established, and the radial and circumferential magnetic flux density distribution characteristics in the bearing air gap are solved, thereby determining the distribution state of the magnetic field in the region where the outer auxiliary bearing ball is located, and calculating the magnetic adsorption load applied by the permanent magnet to the outer auxiliary bearing ball.

[0049] It should be noted that the calculation of the magnetic attraction load exerted by the permanent magnet on the outer auxiliary bearing balls is the equivalent magnetic attraction force of the permanent magnet. The expression is:

[0050] ;

[0051] in, This represents the equivalent magnetic attraction force of a permanent magnet. Indicates the number of permanent magnets. Indicates the magnetic force utilization coefficient. This represents the air gap magnetic flux density. It represents the vacuum permeability.

[0052] S3. Set the various structural parameters of the two-stage tandem rolling bearing, and calculate the frictional torque of the inner and outer rolling elements of the two-stage tandem rolling bearing in combination with magnetic adsorption load;

[0053] Specifically, the structural parameters of a two-stage tandem rolling bearing include: drive power. Input speed Inner ring bearing speed Outer ring bearing speed Pitch circle diameter of inner ring bearing outer ring bearing pitch circle diameter Inner ring bearing normal load The original normal phase load of the outer ring bearing Kinematic viscosity of inner ring bearing lubricating oil Kinematic viscosity of outer ring bearing lubricating oil Lubricating viscosity coefficient Load-related friction coefficient Number of permanent magnets Magnetic utilization coefficient air gap magnetic flux density Vacuum permeability Effective area Equivalent magnetic attraction force Torque of the inner ring bearing independent of load Torque of the outer ring bearing independent of load Torque related to load in inner ring bearing Torque related to load in outer ring bearings and driving force .

[0054] It should be noted that the calculation of the load-independent torque of the inner ring rolling elements, i.e., the inner ring bearing balls, in a two-stage tandem rolling bearing refers to... The expression is:

[0055] when When ≥2000, ;

[0056] when <2000, .

[0057] Calculate the load-independent torque of the outer ring rolling elements, i.e., the outer ring bearing balls, of the two-stage tandem rolling bearing. The expression is:

[0058] when When ≥2000, ;

[0059] when <2000, .

[0060] Furthermore, calculate the load-related torque of the inner ring rolling elements, i.e., the inner ring bearing balls, in a two-stage tandem rolling bearing. The expression is:

[0061] ;

[0062] Calculate the load-related torques of the outer ring rolling elements (i.e., the outer ring bearing balls) of a two-stage tandem rolling bearing. The expression is:

[0063] .

[0064] S4. Calculate the frictional torque generated by the driving force of the two-stage tandem rolling bearing on the inner and outer rolling elements, and output the driving force of the two-stage tandem rolling bearing.

[0065] It should be noted that the calculation of the driving force of a two-stage tandem rolling bearing is the driving force acting on the bearing. The expression is:

[0066] .

[0067] S5. Based on the mechanical principles of rolling bearings, compare and analyze the driving force of the double-stage tandem rolling bearing with the frictional torque of the inner and outer rolling elements, and output the judgment condition for the outer bearing to rotate.

[0068] Specifically, based on the mechanical principles of rolling bearings, and taking into account the driving force of the two-stage tandem rolling bearing and the frictional torque corresponding to the inner and outer rolling elements, a comparison relationship between the driving force and the total frictional torque is established. When the driving torque corresponding to the driving force is greater than or equal to the total frictional torque of the inner and outer rolling elements, it is determined that the outer bearing can overcome the frictional resistance and enter the rotation state, thereby outputting the rotation determination condition of the outer bearing.

[0069] S6. By solving the equations of the driving force and the frictional torque of the inner and outer rolling elements of the two-stage tandem rolling bearing, the relationship between the driving force and the frictional torque of the two-stage tandem rolling bearing is obtained.

[0070] It should be noted that the relationship between the driving force and the frictional torque of a two-stage tandem rolling bearing is as follows:

[0071] .

[0072] In summary, this invention achieves a significant improvement in the rotational performance of the outer bearing by: rationally dividing the structure of a two-stage tandem rolling bearing; establishing a model relating the driving force and frictional torque of the outer bearing; analyzing and determining whether the outer bearing is capable of rotation; and applying auxiliary loads to the rolling elements of the outer bearing through a non-contact magnetic loading method, while fully considering the original mechanical characteristics of the bearing. This enables the outer bearing to achieve stable rotation under startup and light load conditions. This provides a new technical approach and engineering reference for the design and application of two-stage tandem rolling bearings under complex operating conditions.

[0073] It should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and are not intended to limit it. Although the present invention has been described in detail with reference to preferred embodiments, those skilled in the art should understand that modifications or equivalent substitutions can be made to the technical solutions of the present invention without departing from the spirit and scope of the technical solutions of the present invention, and all such modifications or substitutions should be covered within the scope of the claims of the present invention.

Claims

1. A method for assisting the rotation of the outer layer of a two-stage tandem bearing with a permanent magnet additional load, characterized in that: include, The two-stage tandem rolling bearing is divided into two parts: the bearing body and the permanent magnet loading system. The core of the permanent magnet loading system is the permanent magnet unit. Based on the magnetic field distribution formed by the permanent magnet unit in the bearing air gap, the magnetic adsorption load applied by the permanent magnet to the outer auxiliary bearing balls is calculated. Set the various structural parameters of the two-stage tandem rolling bearing, and calculate the frictional torque of the inner and outer rolling elements of the two-stage tandem rolling bearing by combining magnetic adsorption load; Calculate the frictional torque generated by the driving force of the two-stage tandem rolling bearing on the inner and outer rolling elements, and output the driving force of the two-stage tandem rolling bearing; Based on the mechanical principles of rolling bearings, the driving force of a two-stage tandem rolling bearing is compared and analyzed with the frictional torque of the inner and outer rolling elements, and the conditions for determining the rotation of the outer bearing are output. By solving the equations of the driving force and the frictional torque of the inner and outer rolling elements of a two-stage tandem rolling bearing, the relationship between the driving force and the frictional torque of the two-stage tandem rolling bearing is obtained.

2. The method for assisting the outer layer rotation of a two-stage tandem bearing with a permanent magnet additional load as described in claim 1, characterized in that: The bearing body consists of an inner main bearing and an outer auxiliary bearing connected in series, with a permanent magnet loading system embedded in the transition ring between the two-stage series rolling bearings.

3. The method for assisting the outer layer rotation of a two-stage tandem bearing with a permanent magnet additional load as described in claim 1, characterized in that: The core of the permanent magnet loading system is a permanent magnet unit distributed in a Heilbeck array. The magnetic field generated by the permanent magnet unit applies a controllable additional load to the balls of the outer auxiliary bearing.

4. The method for assisting the outer layer rotation of a two-stage tandem bearing with a permanent magnet additional load as described in claim 1, characterized in that: The expression for calculating the magnetic adsorption load applied by the permanent magnet to the outer auxiliary bearing balls is as follows: ； in, This represents the equivalent magnetic attraction force of a permanent magnet. Indicates the number of permanent magnets. Indicates the magnetic force utilization coefficient. This represents the air gap magnetic flux density. Represents the permeability of free space. Indicates the effective area.

5. The method for assisting the outer layer rotation of a two-stage tandem bearing with a permanent magnet additional load as described in claim 1, characterized in that: The structural parameters of the two-stage tandem rolling bearing include: driving power. Input speed Inner ring bearing speed Outer ring bearing speed Pitch circle diameter of inner ring bearing outer ring bearing pitch circle diameter Inner ring bearing normal load The original normal phase load of the outer ring bearing Kinematic viscosity of inner ring bearing lubricating oil Kinematic viscosity of outer ring bearing lubricating oil Lubricating viscosity coefficient Load-related friction coefficient Number of permanent magnets Magnetic utilization coefficient air gap magnetic flux density Vacuum permeability Equivalent magnetic attraction force Torque of the inner ring bearing independent of load Torque of the outer ring bearing independent of load Torque related to load in inner ring bearing Torque related to load in outer ring bearings and driving force .

6. The method for assisting the outer layer rotation of a two-stage tandem bearing with a permanent magnet additional load as described in claim 5, characterized in that: The expression for calculating the torque of the inner ring rolling elements of a two-stage tandem rolling bearing, independent of the load, is as follows: when ≥2000, ; when <2000, .

7. The method for assisting the outer layer rotation of a two-stage tandem bearing with a permanent magnet additional load as described in claim 5, characterized in that: The expression for calculating the torque of the outer ring rolling elements of a two-stage tandem rolling bearing, independent of the load, is as follows: when When ≥2000, ; when <2000, .

8. The method for assisting the outer layer rotation of a two-stage tandem bearing with a permanent magnet additional load as described in claim 5, characterized in that: The calculation of the torque of the inner ring rolling elements of the two-stage tandem rolling bearing in relation to the load. The expression is: ； Calculate the torque of the outer ring rolling elements of a two-stage tandem rolling bearing in relation to the load. The expression is: 。 9. The method for assisting the outer layer rotation of a two-stage tandem bearing with a permanent magnet additional load as described in claim 5, characterized in that: The calculation of the driving force of the two-stage tandem rolling bearing The expression is: 。 10. The method for assisting the outer layer rotation of a two-stage tandem bearing with a permanent magnet additional load as described in claim 5, characterized in that: The relationship between the driving force and the frictional torque of the two-stage tandem rolling bearing is as follows: 。

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