Speed ​​analysis method of multi-stage series rolling bearing based on skeletal muscle micro-bionics

Abstract

The present invention discloses a speed analysis method of a multi-stage tandem rolling bearing based on skeletal muscle micro-bionics, which relates to the field of mechanical transmission technology, including: dividing a three-layer tandem rolling bearing into two double-layer rolling bearings, wherein the two double-layer rolling bearings are respectively a first double-layer rolling bearing composed of a first-level bearing and a second-level bearing, and a second double-layer rolling bearing composed of a second-level bearing and a third-level bearing; calculating the revolution speed of the inner ring rolling element and the outer ring rolling element of the two double-layer rolling bearings, as well as the relative speed relative to their respective middle rings; according to the mechanical principle of the rolling bearing, respectively constructing and solving the torque balance equations of the two double-layer rolling bearings, and obtaining the speed distribution relation of the two double-layer rolling bearings. Through the present invention, the analysis of the speed relationship and distribution law between the bearings at each level of the three-layer tandem rolling bearing is realized.

Description

Technical Field

[0001] The invention relates to the technical field of mechanical transmission, and in particular to a rotation speed analysis method based on skeletal muscle micro-bionic multi-stage series rolling bearings. Background Art

[0002] A two-stage tandem bearing has been proposed for high-speed, high-temperature, and high-stress working environments. Compared with traditional single-stage bearings, the two-stage tandem bearing has a certain improvement in speed. From a kinematic point of view, the middle ring of the two-stage tandem bearing shares a certain speed, and the rotating middle ring distributes the speed to the first-stage bearing, thereby achieving speed distribution, making the two-stage tandem bearing have the advantages of low rolling body movement speed and high bearing limit speed, and can be used in high-speed occasions.

[0003] Since the two-stage tandem bearing has an additional first-stage bearing and an adapter ring compared to the traditional single-stage bearing, its mass increases, which in turn increases the rotational inertia, reduces the system response speed, and increases the machine load. The bearing requires more energy to overcome the friction and inertia caused by its own weight, which limits its application range.

[0004] With the development of science and technology, the speed requirements of various equipment are getting higher and higher, and the speed is a key factor affecting the performance of bearing life, load capacity, vibration and noise. As an advanced form of rolling bearings, multi-stage tandem rolling bearings involve more parameters and factors, and require the comprehensive use of advanced design concepts and methods. However, domestic research in this area is not mature enough, so studying the speed design of multi-stage tandem rolling bearings is an important direction to promote the development of rolling bearing design technology.

[0005] Therefore, a speed design method of a multi-stage series rolling bearing based on the bionic skeletal muscle microstructure is proposed. By referring to the microstructural characteristics of the skeletal muscle micro-bundle layered muscle groups, a multi-stage series rolling bearing is designed. Compared with the traditional two-stage series structure, this structure has a lighter weight and a higher speed on the basis of ensuring the original strength, which solves the problem of limited application range due to large weight or insufficient speed. According to the bearing structure, the present invention proposes a speed analysis method of a multi-stage series rolling bearing based on the bionic skeletal muscle microstructure. The speed analysis method has broad application prospects and can provide theoretical and engineering practice basis for the speed design of new multi-stage bearings. Summary of the invention

[0006] The purpose of the present invention is to provide a speed analysis method for multi-stage tandem rolling bearings based on skeletal muscle micro-bionics, so as to solve the problem in current engineering practice that multi-stage tandem bearings have higher speeds but larger mass than traditional bearings. At the same time, the speed transfer relationship is derived, the speed transfer calculation of multi-stage tandem bearings is realized, and the development of multi-stage rolling bearing design technology is promoted.

[0007] To achieve the above object, the present invention adopts the following technical solutions:

[0008] According to one aspect of the present invention, a rotation speed analysis method of a multi-stage series rolling bearing based on skeletal muscle micro-bionics is provided, which is applied to a three-layer series rolling bearing, comprising:

[0009] The three-layer tandem rolling bearing is divided into two double-layer rolling bearings, wherein the three-layer tandem rolling bearing is composed of an inner layer primary bearing, a middle layer secondary bearing and an outer layer tertiary bearing, and the two double-layer rolling bearings are respectively a No. 1 double-layer rolling bearing composed of a primary bearing and a secondary bearing, and a No. 2 double-layer rolling bearing composed of a secondary bearing and a tertiary bearing, the primary bearing and the tertiary bearing are ball bearings, the secondary bearing is a roller bearing, the roller of the secondary bearing is a bionic hollow roller, the bionic hollow roller imitates the microstructure of skeletal muscle, and the center of the roller is a hollow circle. shaped hole, and a plurality of fan-ring holes are distributed in an annular shape around the circular hole; various structural parameters of the three-layer tandem rolling bearing are set, and the various structural parameters are used to calculate the revolution speeds of the inner ring rolling elements and the outer ring rolling elements of the two double-layer rolling bearings; the relative revolution speeds of the inner ring rolling elements and the outer ring rolling elements of the two double-layer rolling bearings relative to their respective middle rings are calculated; according to the mechanical principles of rolling bearings, the torque balance equations of the two double-layer rolling bearings are respectively constructed; the torque balance equations are solved using the obtained relative speeds to obtain the speed distribution relationship of the two double-layer rolling bearings.

[0010] Optionally, the structural parameters of the three-layer tandem rolling bearing include: the speed of the inner ring of the first-level bearing , Secondary bearing inner ring speed , first-stage bearing outer ring speed , Secondary bearing outer ring speed , rolling element diameter , first-level bearing pitch diameter , Secondary bearing pitch diameter , three-level bearing pitch diameter , first-level bearing contact angle , secondary bearing contact angle , contact angle of three-stage bearing .

[0011] Optionally, calculating the revolution speeds of the inner ring rolling elements and the outer ring rolling elements of the two double-layer rolling bearings includes:

[0012] The revolution speed of the inner ring rolling element of the first double-layer rolling bearing, i.e., the first-level bearing ball, is calculated by the following formula: :

[0013] ;

[0014] The revolution speed of the outer ring rolling element of the first double-layer rolling bearing, i.e., the secondary bearing roller, is calculated by the following formula: :

[0015] ;

[0016] The revolution speed of the inner ring rolling element of the second double-layer rolling bearing, i.e., the secondary bearing roller, is calculated by the following formula: :

[0017] ;

[0018] The revolution speed of the outer ring rolling element of the second double-layer rolling bearing, i.e., the third-level bearing ball, is calculated by the following formula: :

[0019] .

[0020] Optionally, calculating the relative rotational speeds of the inner ring rolling elements and the outer ring rolling elements of the two double-layer rolling bearings relative to their respective middle rings includes:

[0021] The relative speed of the inner ring rolling element of the No. 1 double-layer rolling bearing relative to the middle ring of the No. 1 double-layer rolling bearing is calculated by the following formula: :

[0022] ;

[0023] The middle ring of the No. 1 double-layer rolling bearing is the outer ring of the first-level bearing, that is, the inner ring of the second-level bearing;

[0024] The relative speed of the outer ring rolling element of the No. 1 double-layer rolling bearing relative to the middle ring of the No. 1 double-layer rolling bearing is calculated by the following formula: :

[0025] ;

[0026] The relative speed of the inner ring rolling element of the No. 2 double-layer rolling bearing relative to the middle ring of the No. 2 double-layer rolling bearing is calculated by the following formula: :

[0027] ;

[0028] The middle ring of the second double-layer rolling bearing is the outer ring of the second-level bearing, which is also the inner ring of the third-level bearing;

[0029] The relative speed of the outer ring rolling element of the No. 2 double-layer rolling bearing relative to the middle ring of the No. 2 double-layer rolling bearing is calculated by the following formula: :

[0030] .

[0031] Optionally, constructing the torque balance equations of the two double-layer rolling bearings respectively includes:

[0032] The friction torque balance equation of the No. 1 double-layer rolling bearing is:

[0033] ;

[0034] The friction torque balance equation of the No. 2 double-layer rolling bearing is:

[0035] .

[0036] Optionally, the torque balance equation is solved by using the obtained relative speeds to obtain a speed distribution relationship of the two double-layer rolling bearings, including:

[0037] Substitute the obtained relative speeds into the torque balance equation to obtain the speed distribution of the No. 1 double-layer rolling bearing: for:

[0038] ;

[0039] Speed ​​distribution of the second double-layer rolling bearing for:

[0040] .

[0041] Optionally, a cage is further arranged in the raceway of the secondary bearing, and the cage is composed of two circular rings and a plurality of beams equidistantly distributed in the circumferential direction, the two circular rings are connected by the beams, and each bionic hollow roller is embedded in the space surrounded by two adjacent beams and the circular rings. When the bionic hollow roller rotates, the cage is driven to rotate synchronously, and the revolution speed of the cage is The revolution speed of the secondary bearing roller The same, that is, the expression is:

[0042] .

[0043] In bearing design, maintaining lightweight and high strength has long been a design goal. Traditional bearing designs often use high-strength materials or reduce material usage while pursuing lightweight. Although lightweight is achieved to a certain extent, it is often accompanied by increased costs or reduced mechanical properties. The present invention uses an intermediate layer bearing structure to replace the traditional adapter ring structure of the two-stage tandem bearing, and designs the intermediate layer bearing roller in accordance with the micro-bundle layered muscle group structure of skeletal muscle. While ensuring strength, it not only reduces the overall mass of the bearing, but also reduces the friction and resistance caused by the traditional adapter ring structure, making the bearing rotate more smoothly and the bearing speed increased. The design that imitates the skeletal muscle microstructure provides the roller with additional elastic space, which helps the roller to better adapt to deformation when subjected to force and reduce the risk of wear and damage caused by stress concentration. The present invention also designs a retaining cage in the intermediate layer bearing raceway, which can effectively fix the roller to prevent it from shifting or colliding during rotation, thereby extending the service life of the roller.

[0044] The present invention applies bionic multi-stage tandem rolling bearings and conducts a theoretical analysis of the speed distribution. The two speed distribution relationship equations obtained can be used to calculate the speed distribution ratio through substitution. Through the speed relationship and distribution law between the bearings of each stage, new ideas and methods are provided for the design of bionic bearings and the speed analysis of multi-stage tandem rolling bearings. This theoretical analysis not only helps to optimize the design parameters and performance indicators of the bearings, but also provides strong theoretical support for subsequent experimental research and practical applications. BRIEF DESCRIPTION OF THE DRAWINGS

[0045] Figure 1 It is an overall schematic diagram of a three-layer tandem rolling bearing in the present invention;

[0046] Figure 2 It is a front view of the three-layer tandem rolling bearing in the present invention;

[0047] Figure 3 This is the overall schematic diagram of the first-level bearing;

[0048] Figure 4 It is the overall schematic diagram of the secondary bearing;

[0049] Figure 5 It is the overall schematic diagram of the secondary bearing bionic hollow drum;

[0050] Figure 6 It is the overall schematic diagram of the three-level bearing;

[0051] Figure 7 This is the overall schematic diagram of the outer ring of the secondary bearing;

[0052] Figure 8 It is the overall schematic diagram of the secondary bearing cage;

[0053] Fig. 9 A schematic flow chart of a rotation speed analysis method of a multi-stage series rolling bearing based on skeletal muscle micro-bionics in an embodiment of the present invention;

[0054] Fig.10 It is an overall schematic diagram of a No. 1 double-layer rolling bearing of the present invention;

[0055] Fig.11 It is an overall schematic diagram of the No. 2 double-layer rolling bearing of the present invention;

[0056] Fig.12 This is the total strain contour of the traditional two-stage tandem bearing;

[0057] Fig.13 It is the total strain cloud diagram of the three-layer series rolling bearing in the present invention;

[0058] Fig.14 This is the equivalent stress cloud diagram of the traditional two-stage tandem bearing;

[0059] Fig.15 It is the equivalent stress cloud diagram of the three-layer series rolling bearing in the present invention;

[0060] In the figure: 1. first-level bearing; 2. second-level bearing; 3. third-level bearing; 4. No. 1 double-layer rolling bearing; 5. No. 2 double-layer rolling bearing; 11. first-level ball; 12. first-level bearing inner ring; 13. first-level bearing outer ring; 21. second-level bearing inner ring; 22. second-level bearing outer ring; 23. bionic hollow roller; 24. retaining frame; 31. third-level bearing inner ring; 32. third-level ball; 33. third-level bearing outer ring; 231. circular hole; 232. fan ring hole; 241. first circular ring; 242. second circular ring; 243. beam body; 311. roller raceway of second-level bearing; 312. ball raceway of third-level bearing. DETAILED DESCRIPTION

[0061] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative work are within the scope of protection of the present invention.

[0062] An embodiment of the present invention provides a speed analysis method for a multi-stage tandem rolling bearing based on skeletal muscle micro-bionics, and performs speed distribution using a bearing with a three-layer tandem rolling bearing design. The three-layer tandem rolling bearing has an additional layer of bearing in the middle of the traditional bearing to replace the adapter ring in the traditional two-stage tandem bearing, and the roller of the newly added middle layer bearing is designed as a cylindrical structure with multiple hollow holes, imitating the microstructure of bones, so as to achieve lighter, stronger and more durable bearing performance.

[0063] Specifically, refer to Figures 1 to 6 The three-layer tandem rolling bearing is mainly composed of an inner primary bearing 1, a middle secondary bearing 2 and an outer tertiary bearing 3.

[0064] The primary bearing 1 is located in the innermost layer of the entire bearing structure and adopts a ball bearing design, including a primary ball 11, a primary bearing inner ring 12, and a primary bearing outer ring 13. The primary ball 11 rolls in the raceway surrounded by the primary bearing inner ring 12 and the primary bearing outer ring 13 to achieve the functions of rotation and support. The primary bearing is connected to the rotating shaft when in use.

[0065] The secondary bearing 2 is located in the middle layer of the entire bearing structure, that is, between the primary bearing 1 and the tertiary bearing 3, and adopts a roller bearing design, including a secondary bearing inner ring 21, a secondary bearing outer ring 22 and a bionic hollow roller 23. Figure 5 The bionic hollow drum 23 is a cylindrical structure modeled after the microstructure of skeletal muscle, with a circular hole 231 in the center. The circular hole 231 helps to reduce the weight of the drum and provides additional elastic space for the drum, so that the drum can better adapt to deformation when bearing load. A plurality of fan ring holes 232 are distributed in an equidistant ring around the central circular hole 231. Optionally, the number of the fan ring holes is 4, and the central angle of the fan corresponding to each fan ring hole is 90°. By combining the central circular hole with the annularly distributed fan ring holes, not only a lightweight design is achieved, but also when bearing load, the design of the fan ring holes helps to disperse stress, reduce deformation and wear of the drum, and provide additional lubrication channels or heat dissipation channels.

[0066] The third-level bearing 3 is located at the outermost layer of the entire bearing structure and is generally installed on a bearing seat when in use. Like the first-level bearing, it also adopts a ball bearing design, including a third-level bearing inner ring 31, third-level balls 32 and a third-level bearing outer ring 33.

[0067] The primary bearing outer ring 13 and the tertiary bearing inner ring 31 together constitute the raceway of the bionic hollow roller 23 in the secondary bearing, that is, the primary bearing outer ring 13 is shared by the secondary bearing inner ring 21, and the tertiary bearing inner ring 31 is shared by the secondary bearing outer ring 22.

[0068] Reference Figure 7 , Figure 7It is an overall schematic diagram of the tertiary bearing inner ring 31 (that is, the secondary bearing outer ring 22) of the present invention. As shown in the figure, raceway grooves are provided on both sides of the tertiary bearing inner ring 31, wherein the inner side is the groove of the roller raceway 311 of the secondary bearing, the shape and size of the roller raceway 311 match the bionic hollow roller 23, and is used to accommodate and support the bionic hollow roller 23 in the secondary bearing to roll in the secondary bearing raceway, and the outward side is the groove of the ball raceway 312 of the tertiary bearing, the shape and size of the ball raceway 312 match the tertiary ball 32, and is used to accommodate and support the rolling of the tertiary ball 32 in the tertiary bearing raceway.

[0069] In addition, a retainer 24 is provided in the raceway of the secondary bearing 2 for fixing and supporting the bionic hollow roller 23. Figure 8 As shown, the cage 24 is composed of two circular rings (a first circular ring 241 and a second circular ring 242) and a plurality of beams 243 equidistantly distributed in the circumferential direction. The first circular ring 241 and the second circular ring 242 are closely connected through the beams 243 to form a stable frame. Each bionic hollow roller 23 is embedded in the space surrounded by two adjacent beams and the circular rings. When the bionic hollow roller rotates, the cage 24 is driven to rotate synchronously in the raceway. The cage 24 ensures the stable rotation of the bionic hollow roller 23 in the raceway and prevents unnecessary collision and friction.

[0070] Furthermore, based on the basic structure and working principle of the above-mentioned three-layer tandem rolling bearing, the embodiment of the present invention also provides some specific dimensional data about the above-mentioned three-layer tandem rolling bearing.

[0071] Specifically, the first-level bearing selects a 6403 deep groove ball bearing, including a first-level bearing inner ring, a first-level bearing outer ring and a first-level ball. The diameter of the first-level bearing inner ring is 17mm, the diameter of the first-level bearing outer ring is 62mm, the thickness of the first-level bearing is 17mm, and the diameter of the first-level ball is 11.25mm, with a total of 10. The second-level bearing includes a first-level bearing outer ring, a third-level bearing inner ring, a bionic hollow roller and a retainer. The diameter of the second-level bearing inner ring is 62mm, the diameter of the second-level bearing outer ring is 99.5mm, and the thickness of the second-level bearing is 17mm. The bionic hollow roller in the second-level bearing has an outer diameter of 11.25mm and an inner diameter of 2.8mm (i.e., the diameter of the central circular hole). In the bionic hollow roller, fan ring holes are distributed in an annular manner around the central circular hole, with a width of 1.7mm and a number of 4. Each fan ring hole is equidistant from the central circular hole of the bionic hollow roller, with a distance of 0.7mm, and the distance between adjacent fan ring holes is 2.25mm. There is also a cage in the secondary bearing raceway, which includes two rings and several beams equidistantly distributed in the circumferential direction. The outer diameter of the first and second rings is 73mm, the inner diameter is 69mm, and the number of beams is 16. The inner ring diameter of the third-level bearing is 99.5mm, the outer ring diameter of the third-level bearing is 129.5mm, the diameter of the third-level ball is the same as that of the first-level ball, which is 11.25mm, and the number is 29. The groove width of the roller raceway is 11.25mm and the depth is 1.88mm, and the groove width of the ball raceway is 11.25mm and the depth is 1.88mm.

[0072] Reference Fig. 9 , Fig. 9 FIG. 1 is a flow chart of a rotation speed analysis method of a multi-stage series rolling bearing based on skeletal muscle micro-bionics in an embodiment of the present invention, which is applied to the above-mentioned three-layer series rolling bearing. Fig. 9 As shown, the method comprises the following steps:

[0073] S1, dividing the three-layer tandem rolling bearing into two double-layer rolling bearings;

[0074] The above three-layer tandem rolling bearing is divided into two double-layer rolling bearing units. Figure 10~Figure 11 As shown, the two double-layer rolling bearings are respectively a No. 1 double-layer rolling bearing 4 composed of a first-level bearing and a second-level bearing, and a No. 2 double-layer rolling bearing 5 composed of a second-level bearing and a third-level bearing, wherein the second-level bearing is a shared layer of the two double-layer rolling bearings.

[0075] S2, setting various structural parameters of the three-layer tandem rolling bearing, and using the various structural parameters to calculate the revolution speeds of the inner ring rolling elements and the outer ring rolling elements of the two double-layer rolling bearings;

[0076] The structural parameters of the three-layer tandem rolling bearing include: the speed of the inner ring of the first-level bearing , Secondary bearing inner ring speed , first-stage bearing outer ring speed , Secondary bearing outer ring speed , rolling element diameter , first-level bearing pitch diameter , Secondary bearing pitch diameter , three-level bearing pitch diameter , first-level bearing contact angle , secondary bearing contact angle , contact angle of three-stage bearing , where the diameters of the rollers in the three-layer tandem rolling bearing are the same, that is, the diameters of the balls in the first-level bearing, the rollers in the second-level bearing, and the balls in the third-level bearing are all the same. In addition, the speed of the inner ring of the second-level bearing is , first-stage bearing outer ring speed The two parameters represent the same meaning, but in order to distinguish and maintain the regularity of the formula parameters, different parameter representations are set.

[0077] Then, the revolution speed of the inner ring rolling element of the first double-layer rolling bearing, i.e., the first-level bearing ball, is calculated by the following formula: :

[0078] ;

[0079] Calculate the revolution speed of the outer ring rolling element of the first double-layer rolling bearing, that is, the secondary bearing roller :

[0080] ;

[0081] Calculate the revolution speed of the inner ring rolling element of the second double-layer rolling bearing, that is, the second-level bearing roller :

[0082] ;

[0083] Calculate the revolution speed of the outer ring rolling element of the second double-layer rolling bearing, that is, the third-level bearing ball :

[0084] .

[0085] The revolution speed of the cage The revolution speed of the secondary bearing roller The same, that is:

[0086] .

[0087] S3, calculating the relative rotational speeds of the inner ring rolling elements and the outer ring rolling elements of the two double-layer rolling bearings relative to their respective middle rings;

[0088] The relative speeds of the inner and outer ring rolling elements of the two double-layer rolling bearings relative to their respective middle rings can be obtained by subtracting the speeds of their respective middle rings from the revolution speeds of the inner and outer ring rolling elements of the two double-layer rolling bearings.

[0089] That is, the relative speed of the inner ring rolling element of the No. 1 double-layer rolling bearing relative to the middle ring of the No. 1 double-layer rolling bearing for:

[0090] ;

[0091] Among them, the middle ring of the No. 1 double-layer rolling bearing is the outer ring of the first-level bearing, which is also the inner ring of the second-level bearing;

[0092] The relative speed of the outer ring rolling element of the No. 1 double-layer rolling bearing relative to the middle ring of the No. 1 double-layer rolling bearing for:

[0093] ;

[0094] The relative speed of the inner ring rolling element of the second double-layer rolling bearing relative to the middle ring of the second double-layer rolling bearing for:

[0095] ;

[0096] Among them, the middle ring of the No. 2 double-layer rolling bearing is the outer ring of the second-level bearing, which is also the inner ring of the third-level bearing;

[0097] The relative speed of the outer ring rolling element of the second double-layer rolling bearing relative to the middle ring of the second double-layer rolling bearing for:

[0098] .

[0099] In the above, due to the characteristics of the roller and the ball, The angle is 0 degrees, so The value is 1, and and Not 1.

[0100] S4, constructing the moment balance equations of the two double-layer rolling bearings respectively according to the mechanical principles of the rolling bearing;

[0101] The friction torque balance equation of the No. 1 double-layer rolling bearing is:

[0102] ;

[0103] The friction torque balance equation of the No. 2 double-layer rolling bearing is:

[0104] .

[0105] S5, solving the torque balance equation using the obtained relative speeds to obtain a speed distribution relational equation of the two double-layer rolling bearings;

[0106] Substituting the relative speeds obtained in the previous calculation into the above torque balance equation for solution, the speed distribution relationship of the two double-layer rolling bearings is obtained, where the speed distribution of the first double-layer rolling bearing is for:

[0107] ;

[0108] Speed ​​distribution of the second double-layer rolling bearing for:

[0109] .

[0110] According to the above two speed distribution relationship formulas, the speed distribution ratio is calculated by substitution. Compared with the speed ratio of the traditional two-stage tandem bearing, the three-layer bearing in the embodiment of the present invention is indeed higher than the two-layer bearing, indicating that the maximum speed of the multi-layer bearing is better than that of the double-layer bearing.

[0111] Reference Figures 12 to 15 , are the total strain cloud diagrams and equivalent stress cloud diagrams of the traditional two-stage tandem bearing and the present invention, both of which are the total strain cloud diagrams and equivalent stress cloud diagrams of the bearing simulated in the ANSYS software, among which, Fig.12 This is the total strain cloud diagram of the simulation of the traditional two-stage tandem bearing. The applied axial load is 1000N and the maximum total deformation is 0.0060058mm; Fig.13 This is the total strain cloud diagram for the simulation of a multi-stage tandem rolling bearing. The applied axial load is 1000N and the maximum total deformation is 0.0056759mm. Fig.14 This is the equivalent stress cloud diagram of the simulation of the traditional two-stage tandem bearing. The applied bearing load is 1000N and the maximum equivalent stress is 173.04MPA. Fig.15 This is an equivalent stress cloud diagram for simulating a multi-stage tandem rolling bearing. The applied bearing load is 1000N and the maximum equivalent stress is 125.41MPA. By comparing the simulation results of the traditional two-stage tandem bearing and the multi-stage tandem rolling bearing of the present invention in ANSYS software, it can be seen that the multi-stage tandem rolling bearing has a smaller total deformation and a lower equivalent stress value when subjected to the same axial load, has better anti-deformation ability and lower stress concentration, thereby improving the fatigue life and reliability of the bearing, and has better load-bearing capacity and service life.

[0112] The present invention provides a method for analyzing the speed of a three-layer series rolling bearing by dividing the bearing structure, setting structural parameters, calculating the speed and relative speed, and constructing a torque balance equation for solution. This method not only takes into account the mechanical properties of the bearing, but also incorporates the design concept of bionics, making the bearing more optimized in structure and more excellent in performance.

[0113] The present invention proposes a speed analysis method for a multi-stage tandem rolling bearing based on skeletal muscle micro-bionics. The method adopts a three-layer rolling bearing design and replaces the adapter ring in the traditional two-stage tandem bearing with an intermediate layer secondary bearing structure, thereby simplifying the structure and improving performance. The roller in the secondary bearing is a bionic hollow roller, which imitates the bundled muscle structure of skeletal muscle. The center of the inner diameter of the roller is hollow, and the fan ring holes are distributed in a ring around the inner diameter, so that the multi-stage tandem bearing has a lighter weight than the traditional two-stage tandem bearing. Each bionic hollow roller is embedded in the retaining frame of the secondary bearing and is equidistantly distributed around the outer surface of the outer ring of the tertiary bearing, so that a constant distance is maintained between adjacent bionic hollow rollers, effectively avoiding collision and wear, and improving the strength and maximum speed of the bearing.

[0114] The speed analysis method of the multi-stage tandem rolling bearing of the present invention is proposed for the skeletal muscle micro-bionic multi-stage tandem rolling bearing structure, which solves the problem of the large mass of traditional two-stage tandem bearings and realizes the lightweight and high speed distribution of the multi-stage tandem bearings, providing a theoretical and engineering practice basis for the speed design of new multi-stage bearings.

[0115] It should be noted that it is obvious to those skilled in the art that the present invention is not limited to the details of the above exemplary embodiments, and that the present invention can be implemented in other specific forms without departing from the spirit or essential features of the present invention. Therefore, no matter from which point of view, the embodiments should be regarded as exemplary and non-restrictive, and the scope of the present invention is defined by the appended claims rather than the above description, and it is intended that all changes falling within the meaning and scope of the equivalent elements of the claims are included in the present invention, and any figure mark in the claims should not be regarded as limiting the claims involved.

[0116] The present invention uses specific examples to illustrate the principles and implementation methods of the present invention. The above examples are only used to help understand the method and core ideas of the present invention. At the same time, for those skilled in the art, according to the ideas of the present invention, there will be changes in the specific implementation methods and application scopes. In summary, the content of this specification should not be understood as limiting the present invention.

Claims

1. A speed analysis method for multi-stage series rolling bearings based on skeletal muscle micro-bionics, characterized in that: The method is applied to a three-layer tandem rolling bearing, comprising: The three-layer tandem rolling bearing is divided into two double-layer rolling bearings, wherein the three-layer tandem rolling bearing is composed of an inner primary bearing, a middle secondary bearing and an outer tertiary bearing, and the two double-layer rolling bearings are respectively a No. 1 double-layer rolling bearing composed of a primary bearing and a secondary bearing, and a No. 2 double-layer rolling bearing composed of a secondary bearing and a tertiary bearing, the primary bearing and the tertiary bearing are ball bearings, the secondary bearing is a roller bearing, the roller of the secondary bearing is a bionic hollow roller, the bionic hollow roller imitates the microstructure of skeletal muscle, the center of the roller is a hollow circular hole, and a plurality of fan ring holes are distributed in a ring around the circular hole; Setting various structural parameters of the three-layer tandem rolling bearing, and using the various structural parameters to calculate the revolution speeds of the inner ring rolling elements and the outer ring rolling elements of the two double-layer rolling bearings; Calculating the relative rotational speeds of the inner ring rolling elements and the outer ring rolling elements of the two double-layer rolling bearings relative to their respective middle rings; According to the mechanical principle of rolling bearings, the moment balance equations of the two double-layer rolling bearings are respectively constructed; The torque balance equation is solved using the obtained relative rotational speeds to obtain a rotational speed distribution relationship between the two double-layer rolling bearings.

2. The speed analysis method of multi-stage tandem rolling bearing based on skeletal muscle micro-bionics according to claim 1 is characterized in that: The structural parameters of the three-layer tandem rolling bearing include: the speed of the inner ring of the first-level bearing , Secondary bearing inner ring speed , first-stage bearing outer ring speed , Secondary bearing outer ring speed , rolling element diameter , first-level bearing pitch diameter , Secondary bearing pitch diameter , three-level bearing pitch diameter , first-level bearing contact angle , Secondary bearing contact angle , contact angle of three-stage bearing .

3. The speed analysis method of multi-stage tandem rolling bearing based on skeletal muscle micro-bionics according to claim 2 is characterized in that: Calculating the revolution speeds of the inner ring rolling elements and the outer ring rolling elements of the two double-layer rolling bearings includes: The revolution speed of the inner ring rolling element of the first double-layer rolling bearing, i.e., the first-level bearing ball, is calculated by the following formula: : ； The revolution speed of the outer ring rolling element of the first double-layer rolling bearing, i.e., the secondary bearing roller, is calculated by the following formula: : ； The revolution speed of the inner ring rolling element of the second double-layer rolling bearing, i.e., the secondary bearing roller, is calculated by the following formula: : ； The revolution speed of the outer ring rolling element of the second double-layer rolling bearing, i.e., the third-level bearing ball, is calculated by the following formula: : 。 4. The speed analysis method of multi-stage tandem rolling bearing based on skeletal muscle micro-bionics according to claim 3 is characterized in that: Calculating the relative speeds of the inner ring rolling elements and the outer ring rolling elements of the two double-layer rolling bearings relative to their respective middle rings includes: The relative speed of the inner ring rolling element of the No. 1 double-layer rolling bearing relative to the middle ring of the No. 1 double-layer rolling bearing is calculated by the following formula: : ； The middle ring of the No. 1 double-layer rolling bearing is the outer ring of the first-level bearing, that is, the inner ring of the second-level bearing; The relative speed of the outer ring rolling element of the No. 1 double-layer rolling bearing relative to the middle ring of the No. 1 double-layer rolling bearing is calculated by the following formula: : ； The relative speed of the inner ring rolling element of the No. 2 double-layer rolling bearing relative to the middle ring of the No. 2 double-layer rolling bearing is calculated by the following formula: : ； The middle ring of the second double-layer rolling bearing is the outer ring of the second-level bearing, which is also the inner ring of the third-level bearing; The relative speed of the outer ring rolling element of the No. 2 double-layer rolling bearing relative to the middle ring of the No. 2 double-layer rolling bearing is calculated by the following formula: : 。 5. The speed analysis method of multi-stage series rolling bearing based on skeletal muscle micro-bionics according to claim 4 is characterized in that: The moment balance equations of the two double-layer rolling bearings are constructed respectively, including: The friction torque balance equation of the No. 1 double-layer rolling bearing is: ； The friction torque balance equation of the No. 2 double-layer rolling bearing is: 。 6. The speed analysis method of multi-stage tandem rolling bearing based on skeletal muscle micro-bionics according to claim 5 is characterized in that: The torque balance equation is solved using the obtained relative speeds, and the speed distribution relationship of the two double-layer rolling bearings is obtained, including: Substitute the obtained relative speeds into the torque balance equation to obtain the speed distribution of the No. 1 double-layer rolling bearing: for: ； Speed ​​distribution of the second double-layer rolling bearing for: 。 7. The speed analysis method of multi-stage series rolling bearing based on skeletal muscle micro-bionics according to claim 6 is characterized in that: A cage is also arranged in the raceway of the secondary bearing. The cage is composed of two circular rings and a plurality of beams equidistantly distributed in the circumferential direction. The two circular rings are connected by the beams. Each bionic hollow roller is embedded in the space surrounded by two adjacent beams and the circular rings. When the bionic hollow roller rotates, the cage is driven to rotate synchronously. The revolution speed of the cage is The revolution speed of the secondary bearing roller The same, that is, the expression is: 。

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