Methods, systems, devices, equipment and media for calculating bearings and bearing load distribution

Abstract

This application provides a method, system, apparatus, equipment, and medium for calculating bearing load distribution, relating to the field of bearing load calculation. Applied to a calculation unit used to calculate the bearing load of a composite bearing, the composite bearing including a first outer ring, a second outer ring, an inner ring, a main thrust roller, and an auxiliary thrust roller, the method includes: collecting structural parameters, material parameters, and load parameters of the composite bearing, and applying an external load to the composite bearing based on the load parameters; calculating the mutual approach amount of the first contact pair, the second contact pair, and the third contact pair based on the structural and material parameters; and calculating the load borne by the main thrust roller and the auxiliary thrust roller based on the mutual approach amounts of the first, second, and third contact pairs. This application calculates the load borne by the main thrust roller and the auxiliary thrust roller by using mutual approach amounts, achieving accurate calculation of the bearing load distribution of the composite bearing.

Description

Technical Field

[0001] This application relates to the field of bearing load calculation, and in particular to a method, system, device, equipment and medium for calculating bearings and bearing load distribution. Background Technology

[0002] In the tunnel boring machine (TBM) process, the main bearing plays a crucial role, bearing the axial load, radial load, and overturning moment exerted on the cutterhead by the soil or rock during excavation. Existing TBM main bearings typically consist of three rows of cylindrical roller bearings, comprising an inner ring, two outer rings, three cylindrical roller discs, and a cage. The main thrust rollers bear the axial load and overturning moment, the auxiliary thrust rollers bear the overturning moment, and the radial rollers bear the radial load individually. The overall structure is relatively complex, and further optimization is possible.

[0003] Existing optimized bearings replace the auxiliary thrust rollers and radial rollers of the main bearing with a row of rolling elements capable of simultaneously bearing radial and overturning moment loads. Through the two rows of rolling elements, the main bearing can simultaneously bear axial, radial, and overturning moment loads.

[0004] In the existing technology, the main problem is that the auxiliary push raceway of the bearing is in point contact form, which leads to a weak radial load-bearing capacity of the bearing. Summary of the Invention

[0005] This application provides a bearing and a method, system, device, equipment and medium for calculating bearing load distribution, in order to solve the problem that the auxiliary push raceway of the bearing in the prior art is in the form of point contact, which leads to the weak radial load-bearing capacity of the bearing.

[0006] In a first aspect, this application provides a combined bearing, comprising: a first outer ring, a second outer ring, an inner ring, a main thrust roller, a main thrust cage, an auxiliary thrust roller, and an auxiliary thrust cage;

[0007] The first outer ring and the second outer ring are fastened together to form a whole outer ring, which is then fitted onto the inner ring;

[0008] The upper inner wall of the first outer ring and the upper outer wall of the inner ring are spaced apart to form a main push raceway. The main push roller is installed in the main push raceway through the main push cage. The main push roller is a cylindrical roller. The contact form between the main push roller and the main push raceway is line contact.

[0009] The lower inner wall of the first outer ring, the lower inner wall of the second outer ring, and the lower outer wall of the inner ring are spaced apart to form an auxiliary pusher raceway. The auxiliary pusher rollers are installed in the auxiliary pusher raceway through an auxiliary pusher retainer. The auxiliary pusher rollers are crossed cylindrical rollers, and the contact between the auxiliary pusher rollers and the auxiliary pusher raceway is a line contact.

[0010] In one possible design, the lower inner wall of the first outer ring and the inner wall of the second outer ring are both provided with chamfers, and the two chamfers are spaced apart to form a first right-angled groove rolling surface.

[0011] The lower side of the outer wall of the inner ring is provided with a second right-angle groove rolling surface, and the first right-angle groove rolling surface and the second right-angle groove rolling surface are spaced apart to form an auxiliary push track.

[0012] In one possible design, the main push roller forms line contact with the first outer ring and the inner ring respectively, generating two first contact lines; the two first contact lines form a first contact pair, which is used to bear radial loads and overturning moments.

[0013] The auxiliary push roller forms line contact with the upper half of the first outer ring raceway and the lower half of the inner ring raceway, respectively, and generates two second contact lines. The two second contact lines form a second contact pair, which is used to bear radial load and overturning moment.

[0014] The auxiliary push roller forms line contact with the lower half of the second outer ring raceway and the upper half of the inner ring raceway, respectively, and generates two third contact lines. The two third contact lines form a third contact pair, which is used to bear radial loads and overturning moments.

[0015] In one possible design, the inner ring floats relative to the first outer ring in the radial direction of the inner ring, and the mutual approach of the first contact pair and the second contact pair floats accordingly.

[0016] If the inner ring floats relative to the second outer ring in the radial direction of the inner ring, then the mutual approach amount of the third contact pair will also float.

[0017] Secondly, this application provides a method for calculating bearing load distribution, applied to a calculation unit. The calculation unit is used to calculate the bearing load of a combined bearing, which includes a first outer ring, a second outer ring, an inner ring, a main thrust roller, and an auxiliary thrust roller. The method includes:

[0018] Collect the structural parameters, material parameters, and load parameters of the combined bearing, and apply external loads to the combined bearing based on the load parameters;

[0019] Based on structural and material parameters, the mutual approach of the first contact pair, the second contact pair, and the third contact pair is calculated respectively. The first contact pair is generated by the line contact formed between the main push roller and the first outer ring and the inner ring respectively. The second contact pair is generated by the line contact formed between the upper half of the raceway of the first outer ring and the lower half of the raceway of the inner ring respectively. The third contact pair is generated by the line contact formed between the lower half of the raceway of the second outer ring and the upper half of the raceway of the inner ring respectively. The first, second, and third contact pairs are all used to bear radial loads and overturning moments.

[0020] Based on the mutual approach of the first contact pair, the second contact pair, and the third contact pair, the loads borne by the main push roller and the auxiliary push roller are calculated respectively.

[0021] In one possible design, based on the mutual approach of the first contact pair, the second contact pair, and the third contact pair, the loads borne by the main push roller and the auxiliary push roller are calculated separately, including:

[0022] Based on the mutual approach of the first contact pair, the second contact pair, and the third contact pair, calculate the loads that the first contact pair, the second contact pair, and the third contact pair exert on the inner ring respectively;

[0023] Based on the loads applied to the inner ring by the first contact pair, the second contact pair, and the third contact pair, a mechanical equilibrium analysis is performed on the inner ring to obtain the axial displacement, radial displacement, and angular displacement of the inner ring.

[0024] Based on the axial, radial, and angular displacements of the inner ring, the loads borne by the main push roller and the auxiliary push roller are calculated respectively.

[0025] In one possible design, based on structural and material parameters, the mutual approach amounts of the first contact pair, the second contact pair, and the third contact pair are calculated respectively, including:

[0026] Based on structural and material parameters, the mutual approach amount of the first contact pair is calculated using a first formula; wherein the first formula is:

[0027]

[0028] in, It is the mutual approach quantity of the first contact pair, D pw1 It is the distribution circle diameter of the main pusher roller, θ is the angular displacement, and δ a It is the axial displacement, P a is the axial clearance, m is the number of main push rollers, and i is the i-th roller out of the m rollers. It is the position distribution angle of the i-th roller;

[0029] Based on structural and material parameters, the mutual approach between the inner and outer raceways at the second contact pair is calculated using a second formula; whereby the second formula is:

[0030]

[0031] in, D is the mutual approach amount between the inner and outer raceways at the second contact pair. w2 It is the nominal diameter of the auxiliary push roller; In the position distribution angle The distance between the inner and outer raceways after the auxiliary push roller bears the load;

[0032]

[0033] Where, δ r It is the radial displacement, D pw2 It is the diameter of the distribution circle of the auxiliary push roller;

[0034] A0 = D w +0.5P a sina

[0035] Where A0 is the normal distance between the inner and outer raceways before the auxiliary push roller is loaded; at the second contact pair, the auxiliary push roller with the largest load is used as the reference. The position distribution angle of the i-th auxiliary push roller is represented, and n is the number of auxiliary push rollers;

[0036] Based on structural and material parameters, the mutual approach between the inner and outer raceways at the third contact pair is calculated using a third formula; whereby the third formula is:

[0037]

[0038] in, It is the amount of approach between the inner and outer raceways at the third contact point. In the position distribution angle The distance between the inner and outer raceways after the auxiliary roller bears the load;

[0039]

[0040] At the third contact pair, the auxiliary thrust roller with the largest load is used as the reference. This represents the position distribution angle of the i-th auxiliary push roller.

[0041] In one possible design, a mechanical equilibrium analysis is performed on the inner ring to obtain the axial, radial, and angular displacements of the inner ring, including:

[0042] Based on the static equilibrium equation of the inner ring in the axial direction, the axial displacement of the inner ring is obtained.

[0043] The static equilibrium equation of the inner ring in the axial direction is:

[0044]

[0045] Among them, F a It is the axial load borne by the inner ring;

[0046] The radial displacement of the inner ring is obtained based on the static equilibrium equation of the inner ring in the radial direction.

[0047] The static equilibrium equation of the inner ring in the radial direction is:

[0048]

[0049] Among them, F r It is the radial load borne by the inner ring;

[0050] The angular displacement of the inner ring is obtained based on the static equilibrium equation of the inner ring in the direction of rotation of the inner ring.

[0051] The static equilibrium equation of the inner ring in the direction of rotation of the inner ring is:

[0052]

[0053] Among them, M k It is the overturning moment load borne by the inner ring, d c It is the distance between the distribution plane of the main push raceway and the distribution plane of the auxiliary push raceway.

[0054] Thirdly, this application provides a bearing load distribution calculation system, comprising:

[0055] A combined bearing and a calculation unit, the calculation unit being used to execute the load distribution calculation method of the load distribution calculation system.

[0056] Fourthly, this application provides a bearing load distribution calculation device, comprising:

[0057] Acquisition module, processing module, and calculation module;

[0058] The data acquisition module is used to collect structural parameters, material parameters, and load parameters of the combined bearing.

[0059] The processing module is used to apply external loads to the combined bearing based on load parameters;

[0060] The calculation module is used to calculate the mutual approach of the first contact pair, the second contact pair, and the third contact pair based on structural parameters and material parameters. The first contact pair is generated by the line contact formed between the main thrust roller and the first outer ring and the inner ring, respectively. The second contact pair is generated by the line contact formed between the first outer ring and the inner ring, respectively. The third contact pair is generated by the line contact formed between the second outer ring and the inner ring, respectively. The first contact pair, the second contact pair, and the third contact pair are all used to bear radial loads and overturning moments.

[0061] The calculation module is also used to calculate the loads borne by the main push roller and the auxiliary push roller based on the mutual approach of the first contact pair, the second contact pair and the third contact pair respectively.

[0062] Fifthly, this application provides an electronic device, including: a processor, and a memory communicatively connected to the processor;

[0063] The memory stores instructions that the computer executes;

[0064] When the processor executes computer execution instructions stored in memory, it is used to implement the bearing load distribution calculation method as described in any of the second aspects.

[0065] In a sixth aspect, this application provides a computer-readable storage medium storing computer-executable instructions, which, when executed by a processor, are used to implement the bearing load distribution calculation method as described in any of the second aspects.

[0066] In a seventh aspect, this application provides a computer program product, including a computer program that, when executed by a processor, implements the bearing load distribution calculation method as described in any of the second aspects.

[0067] This application provides a bearing and a method, system, device, equipment, and medium for calculating bearing load distribution. Applied to a calculation unit, the calculation unit calculates the bearing load of a combined bearing, which includes a first outer ring, a second outer ring, an inner ring, a main thrust roller, and an auxiliary thrust roller. The method includes: collecting structural parameters, material parameters, and load parameters of the combined bearing; applying an external load to the combined bearing based on the load parameters; calculating the mutual approach of the first contact pair, the second contact pair, and the third contact pair based on the structural and material parameters; and calculating the load borne by the main thrust roller and the auxiliary thrust roller based on the mutual approach of the first contact pair, the second contact pair, and the third contact pair. The combined bearing provided in this application reduces the number of raceway rows, the number of rolling elements, and the bearing thickness, thereby reducing the structural complexity of the bearing and making the main bearing more reliable and compact. Simultaneously, by adding a cross-cylindrical roller structure to the auxiliary thrust raceway, the bearing's radial load and overturning moment carrying capacity is improved, solving the technical problem of weak radial load carrying capacity of the bearing. The bearing load distribution calculation method provided in this application calculates the load borne by the main push roller and the auxiliary push roller by mutual approximation, thereby achieving accurate calculation of the bearing load distribution of the combined bearing. Attached Figure Description

[0068] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0069] Figure 1 A schematic diagram of a bearing load distribution calculation system architecture provided in this application embodiment;

[0070] Figure 2 This is a schematic diagram of the structure of a combined bearing provided in an embodiment of this application;

[0071] Figure 3 A schematic diagram of force analysis for a combined bearing provided in an embodiment of this application;

[0072] Figure 4 A flowchart illustrating a bearing load distribution calculation method provided in this application embodiment. Figure 1 ;

[0073] Figure 5 A flowchart illustrating a bearing load distribution calculation method provided in this application embodiment. Figure 2 ;

[0074] Figure 6 A flowchart illustrating a bearing load distribution calculation method provided in this application embodiment. Figure 3 ;

[0075] Figure 7 A flowchart illustrating a bearing load distribution calculation method provided in this application embodiment. Figure 4 ;

[0076] Figure 8 This is a schematic diagram of the load distribution at the first contact pair provided in an embodiment of this application;

[0077] Figure 9 This is a schematic diagram of the load distribution at the second contact pair provided in an embodiment of this application;

[0078] Figure 10 This is a schematic diagram of the load distribution at the third contact pair provided in an embodiment of this application;

[0079] Figure 11 This is a schematic diagram of the structure of a bearing load distribution calculation system provided in an embodiment of this application;

[0080] Figure 12 This is a schematic diagram of the structure of a bearing load distribution calculation device provided in an embodiment of this application;

[0081] Figure 13 This is a schematic diagram of a bearing load distribution calculation device provided in an embodiment of this application.

[0082] Figure label:

[0083] 11-Data acquisition equipment; 12-Processing equipment; 13-Display equipment;

[0084] 20 - Combined bearing; 21 - First outer ring; 22 - Second outer ring; 23 - Inner ring; 24 - Main thrust roller; 25 - Main thrust cage; 26 - Auxiliary thrust roller; 27 - Auxiliary thrust cage;

[0085] 112 - Computational Unit;

[0086] 130 - Electronic device; 131 - Processor; 132 - Memory; 133 - Communication component; 134 - Bus. Detailed Implementation

[0087] Exemplary embodiments will now be described in detail, examples of which are illustrated in the accompanying drawings. When the following description relates to the drawings, unless otherwise indicated, the same numerals in different drawings represent the same or similar elements. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with this application. Rather, they are merely examples of devices and methods consistent with some aspects of this application as detailed in the appended claims, and not all embodiments. All other embodiments obtained by those skilled in the art based on the embodiments of this invention without inventive effort are within the scope of protection of this invention.

[0088] In the embodiments of this application, the terms "first" and "second" are used to distinguish identical or similar items with essentially the same function and effect. Those skilled in the art will understand that the terms "first" and "second" do not limit the quantity or execution order, and that the terms "first" and "second" do not necessarily imply that they are different.

[0089] It should be noted that in the embodiments of this application, the words "exemplary" or "for example" are used to indicate examples, illustrations, or explanations. Any embodiment or design scheme described as "exemplary" or "for example" in this application should not be construed as being more preferred or advantageous than other embodiments or design schemes. Specifically, the use of the words "exemplary" or "for example" is intended to present the relevant concepts in a specific manner. In the embodiments of this application, "at least one" refers to one or more, and "more than one" refers to two or more.

[0090] It should be noted that the phrase "at...time" in the embodiments of this application can refer to the instant at which a certain situation occurs, or to a period of time after the occurrence of a certain situation; the embodiments of this application do not specifically limit this. Furthermore, the bearing load distribution calculation method provided in the embodiments of this application is merely an example, and the bearing load distribution calculation method may include more or fewer elements.

[0091] A tunnel boring machine (TBM) is an engineering machine used for tunnel excavation. It integrates mechanical, electrical, hydraulic, and information technology, enabling it to excavate long-distance, deep, and large-diameter tunnels. It can adapt to harsh working environments, and its automated and intelligent operation results in high efficiency and minimal human intervention, significantly reducing the workload of construction workers. During tunnel excavation, the main bearing plays a crucial role, bearing the axial load, radial load, and overturning moment exerted on the cutterhead by the soil or rock.

[0092] Existing tunneling machine main bearings are generally three-row cylindrical roller bearings, consisting of an inner ring, two outer rings, three discs of cylindrical rollers, and a cage. The main thrust rollers bear the axial load and overturning moment, the auxiliary thrust rollers bear the overturning moment, and the radial rollers bear the radial load separately. The overall structure is relatively complex and there is potential for further optimization.

[0093] To address the aforementioned drawbacks, existing technologies primarily replace the auxiliary thrust rollers and radial rollers of the main bearing with a row of rolling elements capable of simultaneously bearing radial and overturning moment loads. This eliminates the need for a separate row of radial rollers for radial loads; only two rows of rolling elements are required to enable the main bearing to simultaneously bear axial, radial, and overturning moment loads, with a stronger axial load-bearing capacity.

[0094] The auxiliary push raceway is equipped with a row of four-point contact ball-shaped rolling elements. Because the auxiliary push raceway is in point contact form, the radial load capacity of the bearing is relatively weak.

[0095] Based on this, in order to solve the above-mentioned technical problems, embodiments of this application provide bearings and bearing load distribution calculation methods, systems, devices, equipment, and media, which can be used in the field of bearing load calculation. The inventive concept of this application is as follows: two rows of raceways are arranged inside the bearing; a row of cylindrical rolling elements is arranged on the main pushing raceway, and a row of crossed cylindrical rolling elements is arranged on the auxiliary pushing raceway. Since the contact angle of the crossed cylindrical rollers is not equal to 0, the bearing can withstand radial loads and overturning moments. Furthermore, since the auxiliary pushing raceway is of line contact type, the radial load-bearing capacity is improved.

[0096] Optional, Figure 1 This is a schematic diagram of a bearing load distribution calculation system architecture provided in an embodiment of this application. The application data processing system is a computer device. Figure 1 In the above architecture, at least one of data acquisition device 11, processing device 12 and display device 13 is included.

[0097] It is understood that the structure illustrated in the embodiments of this application does not constitute a specific limitation on the architecture of the bearing load distribution calculation system. In other feasible embodiments of this application, the above architecture may include more or fewer components than illustrated, or combine some components, or split some components, or arrange different components, which can be determined according to the actual application scenario and is not limited here. Figure 1 The components shown can be implemented in hardware, software, or a combination of both.

[0098] In the specific implementation process, the data acquisition device 11 can transmit the acquired data to the processing device 12 through a wired data transmission device or a wireless data transmission device.

[0099] The processing device 12 can calculate the mutual approach of the first contact pair, the second contact pair, and the third contact pair based on the structural and material parameters collected by the data acquisition device 11. By calculating the mutual approach of the first contact pair, the second contact pair, and the third contact pair, and by performing a mechanical balance analysis on the inner ring, the axial displacement, radial displacement, and angular displacement of the inner ring can be obtained, and then the load borne by the main push roller and the auxiliary push roller can be calculated.

[0100] Display device 13 can also be a touch screen or the screen of a terminal device, used to receive user commands while displaying the above-mentioned content, so as to realize interaction with the user.

[0101] It should be understood that the aforementioned processing device can be implemented by a processor reading instructions from memory and executing those instructions, or it can be implemented by a chip circuit.

[0102] Furthermore, the network architecture and business scenarios described in the embodiments of this application are for the purpose of more clearly illustrating the technical solutions of the embodiments of this application, and do not constitute a limitation on the technical solutions provided in the embodiments of this application. As those skilled in the art will know, with the evolution of network architecture and the emergence of new business scenarios, the technical solutions provided in the embodiments of this application are also applicable to similar technical problems.

[0103] The technical solution of this application and how the technical solution of this application solves the above-mentioned technical problems are described in detail below with specific embodiments. These specific embodiments can be combined with each other, and the same or similar concepts or processes may not be described again in some embodiments. The embodiments of this application will now be described with reference to the accompanying drawings.

[0104] Figure 2 This is a schematic diagram of a combined bearing provided in an embodiment of this application. Figure 2 As shown, the combined bearing 20 includes a first outer ring 21, a second outer ring 22, an inner ring 23, a main thrust roller 24, a main thrust cage 25, an auxiliary thrust roller 26, and an auxiliary thrust cage 27.

[0105] The first outer ring 21 and the second outer ring 22 are fastened together to form a whole outer ring and are fitted onto the inner ring 23.

[0106] Specifically, the first outer ring 21 and the second outer ring 22 are fixedly connected to form a whole outer ring, which is then fitted onto the inner ring 23.

[0107] The upper inner wall of the first outer ring 21 and the upper outer wall of the inner ring 23 are spaced apart to form a main push raceway. The main push roller 24 is installed in the main push raceway through the main push retainer 25. The main push roller 24 is a cylindrical roller, and the contact form between the main push roller 24 and the main push raceway is line contact.

[0108] Specifically, the main push roller 24 is installed in the main push raceway through the main push cage 25, and the multiple main push rollers 24 are distributed and arranged through the isolation of the main push cage 25.

[0109] More specifically, the main push roller 24 is a cylindrical roller. When the bearing is under load, the main push roller 24 and the main push raceway are in line contact, which is used to bear axial load and overturning moment.

[0110] In this design, the lower inner wall of the first outer ring 21, the lower inner wall of the second outer ring 22, and the lower outer wall of the inner ring 23 are spaced apart to form an auxiliary pusher raceway. The auxiliary pusher roller 26 is installed in the auxiliary pusher raceway through the auxiliary pusher retainer 27. The auxiliary pusher roller 26 is a cross cylindrical roller, and the contact form between the auxiliary pusher roller 26 and the auxiliary pusher raceway is a line contact.

[0111] Specifically, the auxiliary push rollers 26 are installed in the auxiliary push raceway through the auxiliary push retainer 27, and the auxiliary push rollers 26 are distributed and arranged through the isolation of the auxiliary push retainer 27.

[0112] More specifically, the auxiliary thrust roller 26 is a crossed cylindrical rolling element. When the bearing is under load, the contact between the auxiliary thrust roller 26 and the auxiliary thrust raceway is a line contact, which is used to bear radial load and overturning moment.

[0113] The inner wall of the first outer ring 21 and the inner wall of the second outer ring 22 are both provided with chamfers, and the two chamfers are spaced apart to form a first right-angle groove rolling surface.

[0114] Among them, the lower side of the outer wall of the inner ring 23 is provided with a second right-angle groove rolling surface, and the first right-angle groove rolling surface and the second right-angle groove rolling surface are spaced apart to form an auxiliary push track.

[0115] In this embodiment, the auxiliary push roller 26 is a crossed cylindrical roller, and the internal structure of the combined bearing 20 uses rollers arranged perpendicularly to each other at 90°. Spacers or separators are installed between the rollers to prevent tilting or friction between them, thereby effectively preventing an increase in rotational torque. Simultaneously, the inner and outer rings are segmented, and the clearance is adjustable, allowing for high-precision rotational motion even under preload. Furthermore, this bearing has a minimized overall size and high rigidity, making it ideal for withstanding loads in various directions.

[0116] Figure 3 This is a schematic diagram illustrating the force analysis of a combined bearing provided in an embodiment of this application. Figure 3 As shown:

[0117] Among them, the main pusher roller 24 forms line contact with the first outer ring 21 and the inner ring 23 respectively, and generates two first contact lines; the two first contact lines form a first contact pair, which is used to bear radial load and overturning moment.

[0118] Among them, the auxiliary push roller 26 forms line contact with the upper half of the raceway of the first outer ring 21 and the lower half of the raceway of the inner ring 23, respectively, and generates two second contact lines. The two second contact lines form a second contact pair, which is used to bear radial load and overturning moment.

[0119] Among them, the auxiliary push roller 26 forms line contact with the lower half of the raceway of the second outer ring 22 and the upper half of the raceway of the inner ring 23, respectively, and generates two third contact lines. The two third contact lines form a third contact pair, which is used to bear radial load and overturning moment.

[0120] Specifically, the first contact pair, the second contact pair, and the third contact are all line contacts with multiple contact points, which increases the load-bearing capacity of the main push raceway and the auxiliary push raceway.

[0121] Among them, the inner ring 23 floats relative to the first outer ring 21 in the radial direction of the inner ring 23, and the mutual approach amount of the first contact pair and the second contact pair floats.

[0122] Among them, the inner ring 23 floats relative to the second outer ring 22 in the radial direction of the inner ring 23, and the mutual approach amount of the third contact pair floats.

[0123] In this embodiment, the first outer ring 21 and the second outer ring 22 are fastened together to form a single outer ring, which is fitted onto the inner ring 23, thus forming two rows of raceways. Cylindrical rollers are arranged on the main push raceway, and crossed cylindrical rollers are arranged on the auxiliary push raceway. Since the contact angle of the crossed cylindrical rollers is not equal to 0, the bearing can withstand radial loads and overturning moments. At the same time, because the auxiliary push raceway is composed of crossed cylindrical rollers, compared to the point contact between ball rollers and the raceway (only one contact point), the crossed cylindrical rollers have multiple line contact points with the raceway. The increase in contact points improves the radial load-bearing capacity of the combined bearing, thereby improving the working efficiency of the combined bearing.

[0124] Figure 4 A flowchart illustrating a bearing load distribution calculation method provided in this application embodiment. Figure 1 ,like Figure 3 As shown, this method is applied to a calculation unit, which is used to calculate the bearing load of a combined bearing. The combined bearing includes: a first outer ring, a second outer ring, an inner ring, a main thrust roller, and an auxiliary thrust roller. The method includes:

[0125] S401. Collect the structural parameters, material parameters, and load parameters of the combined bearing, and apply external loads to the combined bearing based on the load parameters.

[0126] S402. Based on structural and material parameters, calculate the mutual approach of the first contact pair, the second contact pair, and the third contact pair respectively.

[0127] The first contact pair is generated by the line contact formed between the main push roller and the first outer ring and inner ring respectively.

[0128] The second contact pair is generated by the line contact formed between the upper half of the outer ring raceway and the lower half of the inner ring raceway.

[0129] The third contact pair is generated by the line contact formed by the lower half of the raceway of the second outer ring and the upper half of the raceway of the inner ring.

[0130] The first contact pair, the second contact pair, and the third contact pair are all used to bear radial loads and overturning moments.

[0131] In this embodiment, since the first contact pair, the second contact pair, and the third contact pair are all in line contact between the inner raceway and the outer raceway, and each has multiple contact points, the force situation between the inner raceway and the outer raceway inside the bearing is reflected by calculating the mutual approach amount.

[0132] S403. Based on the mutual approach of the first contact pair, the second contact pair, and the third contact pair, calculate the loads borne by the main push roller and the auxiliary push roller respectively.

[0133] In this embodiment, based on the mutual approach of the first contact pair, the second contact pair, and the third contact pair between the inner raceway and the outer raceway, the loads borne by the main push roller and the auxiliary push roller are calculated respectively, that is, the loads of the first contact pair, the second contact pair, and the third contact pair on the inner ring respectively.

[0134] This embodiment provides a method for calculating the load distribution of a combined bearing. The method is applied to a calculation unit to calculate the bearing load of the combined bearing, which includes a first outer ring, a second outer ring, an inner ring, a main thrust roller, and an auxiliary thrust roller. The method includes: collecting structural parameters, material parameters, and load parameters of the combined bearing; applying an external load to the combined bearing based on the load parameters; calculating the mutual approach of the first contact pair, the second contact pair, and the third contact pair based on the structural and material parameters; and calculating the load borne by the main thrust roller and the auxiliary thrust roller based on the mutual approach of the first contact pair, the second contact pair, and the third contact pair. The combined bearing provided in this application reduces the number of raceway rows, the number of rolling elements, and the bearing thickness, thereby reducing the structural complexity of the bearing and making the main bearing more reliable and compact. Simultaneously, by adding a cross-cylindrical roller structure to the auxiliary thrust raceway, the bearing's radial load and overturning moment carrying capacity is improved, solving the technical problem of weak radial load carrying capacity of the bearing. The bearing load distribution calculation method provided in this application calculates the load borne by the main push roller and the auxiliary push roller by mutual approximation, thereby achieving accurate calculation of the bearing load distribution of the combined bearing.

[0135] Figure 5 A flowchart illustrating a bearing load distribution calculation method provided in this application embodiment. Figure 2 ,exist Figure 4 Based on the embodiments, such as Figure 5 As shown, the specific implementation steps of S403 above include:

[0136] S501. Based on the mutual approach of the first contact pair, the second contact pair, and the third contact pair, calculate the loads acting on the inner ring by the first contact pair, the second contact pair, and the third contact pair, respectively.

[0137] S502. Based on the loads applied to the inner ring by the first contact pair, the second contact pair, and the third contact pair, a mechanical equilibrium analysis is performed on the inner ring to obtain the axial displacement, radial displacement, and angular displacement of the inner ring.

[0138] Specifically, when the combined bearing only bears axial load, the first and second contact pairs are loaded. When it only bears radial load, the second and third contact pairs are loaded. When it only bears overturning moment, the first, second, and third contact pairs are all loaded. Therefore, when the combined bearing bears any form of external load, the combined bearing can generate loads at the contact pairs to mechanically balance the external load.

[0139] S503. Based on the axial displacement, radial displacement and angular displacement of the inner ring, calculate the loads borne by the main push roller and the auxiliary push roller respectively.

[0140] Optionally, the calculated axial displacement can be substituted into the following:

[0141]

[0142] in, The load acting on the inner ring of the bearing during the first contact pair. It is the mutual approach quantity of the first contact pair.

[0143] Among them, K m It is the line contact elastic deformation constant, which can be expressed as:

[0144]

[0145] Where E1 is the elastic modulus of the raceway material, the unit is (N / mm). 2 v1 is the Poisson's ratio of the raceway material; E2 is the elastic modulus of the roller material, in N / mm². 2 ) is v2, which is the Poisson's ratio of the roller material; L we1 It refers to the effective length of the main cylindrical roller, and the unit is (mm).

[0146] Optionally, the calculated radial displacement can be substituted into the equation:

[0147]

[0148] in, The load acting on the inner ring is the second contact pair. It is the mutual approach quantity of the first contact pair.

[0149] Among them, K s It is the line contact elastic deformation constant, which can be expressed as:

[0150]

[0151] Among them, L we2 It is the effective length of the auxiliary push roller, in mm.

[0152] Optionally, the calculated angular displacement can be substituted into the equation:

[0153]

[0154] in, The load is the third contact pair acting on the inner ring. It is the mutual approach quantity of the first contact pair.

[0155] It should be noted that, based on the loads acting on the inner ring by the first, second, and third contact pairs, a schematic diagram of the load distribution at each contact pair can be obtained, as shown below. Figures 8 to 9 As shown.

[0156] As one example, Figure 8 This is a schematic diagram of the load distribution at the first contact pair provided in an embodiment of this application.

[0157] As one example, Figure 9 This is a schematic diagram of the load distribution at the second contact pair provided in an embodiment of this application.

[0158] As one example, Figure 10 This is a schematic diagram of the load distribution at the third contact pair provided in an embodiment of this application.

[0159] In this embodiment, the application calculates the load at the contact point by the mutual approach amount, and performs a mechanical balance analysis based on the mutual approach amount and the load at the contact point to obtain the axial displacement, radial displacement, and angular displacement of the inner ring, thereby obtaining the load borne by the main push roller and the auxiliary push roller. Compared with the prior art, which calculates the load by the deformation of the main push roller and the auxiliary push roller, the deformation mainly focuses on the shape or size change of the bearing after being subjected to force, which is easily affected by measurement errors and external factors. The mutual approach amount, on the other hand, focuses on the relative position change between the internal components of the bearing, and can more directly reflect the actual operating state of the bearing.

[0160] Figure 6 A flowchart illustrating a bearing load distribution calculation method provided in this application embodiment. Figure 3 ,exist Figure 4 and Figure 5 Based on the embodiments, such as Figure 6 As shown, the specific implementation steps of S402 above include:

[0161] S601. Based on structural parameters and material parameters, calculate the mutual approach amount of the first contact pair using the first formula.

[0162] The first formula is:

[0163]

[0164] in, It is the mutual approach quantity of the first contact pair, D pw1 It is the distribution circle diameter of the main pusher roller, θ is the angular displacement, and δ a It is the axial displacement, P a is the axial clearance, m is the number of main push rollers, and i is the i-th roller out of the m rollers. It is the position distribution angle of the i-th roller.

[0165] It should be noted that, based on the mutual approach of the first contact pair, the load acting on the inner ring of the composite bearing by the first contact pair can be calculated:

[0166]

[0167] in, It is the load that the first contact pair applies to the inner ring of the bearing.

[0168] Among them, K m It is the line contact elastic deformation constant, which can be expressed as:

[0169]

[0170] Where E1 is the elastic modulus of the raceway material, the unit is (N / mm). 2 v1 is the Poisson's ratio of the raceway material; E2 is the elastic modulus of the roller material, in N / mm². 2 ) is v2, which is the Poisson's ratio of the roller material; L we1 It refers to the effective length of the main cylindrical roller, and the unit is (mm).

[0171] S602. Based on structural and material parameters, the mutual approach between the inner and outer raceways at the second contact pair is calculated using the second formula.

[0172] The second formula is:

[0173]

[0174] in, D is the mutual approach amount between the inner and outer raceways at the second contact pair. w2 It is the nominal diameter of the auxiliary push roller; In the position distribution angle The distance between the inner and outer raceways after the auxiliary push roller bears the load;

[0175]

[0176] Where, δ r It is the radial displacement, D pw2 It is the diameter of the distribution circle of the auxiliary push roller;

[0177] A0 = D w +0.5P a sina

[0178] Where A0 is the normal distance between the inner and outer raceways before the auxiliary push roller is loaded; at the second contact pair, the auxiliary push roller with the largest load is used as the reference. The position distribution angle of the i-th auxiliary push roller is represented by , and n is the number of auxiliary push rollers.

[0179] It should be noted that, based on the mutual approach of the second contact pair, the load exerted by the second contact pair on the inner ring of the composite bearing can be calculated:

[0180]

[0181] in, It is the load that the second contact pair applies to the inner ring.

[0182] Among them, K s It is the line contact elastic deformation constant, which can be expressed as:

[0183]

[0184] Among them, L we2 It is the effective length of the auxiliary push roller, in mm.

[0185] S603. Based on structural and material parameters, the mutual approach between the inner and outer raceways at the third contact pair is calculated using the third formula.

[0186] The third formula is:

[0187]

[0188] in, It is the amount of approach between the inner and outer raceways at the third contact point. In the position distribution angle The distance between the inner and outer raceways after the auxiliary roller bears the load;

[0189]

[0190] At the third contact pair, the auxiliary thrust roller with the largest load is used as the reference. This represents the position distribution angle of the i-th auxiliary push roller.

[0191] It should be noted that, based on the mutual approach of the third contact pair, the load exerted by the third contact pair on the inner ring of the composite bearing can be calculated:

[0192]

[0193] in, It is the load that the third contact pair applies to the inner ring.

[0194] In this embodiment, the load acting on the inner ring of the composite bearing is calculated based on the mutual approach amount of the contact pairs. The mutual approach amount directly reflects the fit between the internal components of the bearing, is less susceptible to measurement errors and external factors, and the load calculated based on the mutual approach amount is more accurate, more directly reflecting the actual operating state of the bearing. Simultaneously, the axial clearance P of the composite bearing is also considered. a And the distance d between the distribution surfaces of the main push raceway and the auxiliary push raceway c This study examines the impact on the load distribution of the turntable bearing, thereby improving the accuracy of load distribution calculations.

[0195] Figure 7 A flowchart illustrating a bearing load distribution calculation method provided in this application embodiment. Figure 4 ,exist Figure 4 , Figure 5 as well as Figure 6 Based on the embodiments, such as Figure 7 As shown, the specific implementation steps of S502 above include:

[0196] S701. Based on the static equilibrium equation of the inner ring in the axial direction, the axial displacement of the inner ring is obtained.

[0197] The static equilibrium equation of the inner ring in the axial direction is:

[0198]

[0199] Among them, F a It is the axial load borne by the inner ring, and the unit is (mm).

[0200] Specifically, the axial displacement of the inner ring can be obtained by using the quasi-Newton method.

[0201] S702. Based on the static equilibrium equation of the inner ring in the radial direction, the radial displacement of the inner ring is obtained.

[0202] The static equilibrium equation for the inner ring in the radial direction is:

[0203]

[0204] Among them, F r It is the radial load borne by the inner ring, and the unit is (mm).

[0205] Specifically, the radial displacement of the inner ring can be obtained by using the quasi-Newton method.

[0206] S703. Based on the static equilibrium equation of the inner ring in the direction of rotation of the inner ring, the angular displacement of the inner ring is obtained.

[0207] The static equilibrium equation for the inner ring in the direction of rotation is:

[0208]

[0209] Among them, M k It is the overturning moment load borne by the inner ring, with units of (N·mm); d c It is the distance between the distribution plane of the main push raceway and the distribution plane of the auxiliary push raceway, in mm.

[0210] Specifically, the angular displacement of the inner ring can be obtained by using the quasi-Newton method.

[0211] In this embodiment, considering the axial clearance and the distance between the raceway planes, the mechanical equilibrium equations of the combined bearing are solved using the quasi-Newton method to further verify the rationality of the bearing structure.

[0212] Figure 11 This is a schematic diagram of the structure of a bearing load distribution calculation system provided in an embodiment of this application, as shown below. Figure 11 As shown, the system includes: a combined bearing 20 and a computing unit 112.

[0213] The calculation unit 112 is used to collect the structural parameters, material parameters and load parameters of the combined bearing 20.

[0214] The calculation unit 112 is also used to apply external loads to the combined bearing 20 based on load parameters.

[0215] The calculation unit 112 is also used to calculate the mutual approach of the first contact pair, the second contact pair and the third contact pair respectively based on structural parameters and material parameters; wherein, the first contact pair is generated by the line contact formed between the main push roller and the first outer ring and the inner ring respectively, the second contact pair is generated by the line contact formed between the first outer ring and the inner ring respectively, and the third contact pair is generated by the line contact formed between the second outer ring and the inner ring respectively. The first contact pair, the second contact pair and the third contact pair are all used to bear radial load and overturning moment.

[0216] The calculation unit 112 is also used to calculate the loads borne by the main push roller and the auxiliary push roller based on the mutual approach of the first contact pair, the second contact pair and the third contact pair respectively.

[0217] Figure 12This is a schematic diagram of the structure of a bearing load distribution calculation device provided in an embodiment of this application, as shown below. Figure 12 As shown, the device includes: a data acquisition module 121, a processing module 122, and a calculation module 123.

[0218] The acquisition module 121 is used to acquire the structural parameters, material parameters and load parameters of the combined bearing.

[0219] Processing module 122 is used to apply external loads to the combined bearing based on load parameters.

[0220] The calculation module 123 is used to calculate the mutual approach of the first contact pair, the second contact pair and the third contact pair based on structural parameters and material parameters. The first contact pair is generated by the line contact formed between the main push roller and the first outer ring and the inner ring respectively. The second contact pair is generated by the line contact formed between the first outer ring and the inner ring respectively. The third contact pair is generated by the line contact formed between the second outer ring and the inner ring respectively. The first contact pair, the second contact pair and the third contact pair are all used to bear radial load and overturning moment.

[0221] The calculation module 123 is also used to calculate the loads borne by the main push roller and the auxiliary push roller based on the mutual approach of the first contact pair, the second contact pair and the third contact pair respectively.

[0222] In one possible design, the calculation module 123 is also used to calculate the loads of the first contact pair, the second contact pair, and the third contact pair on the inner ring respectively, based on the mutual approach of the first contact pair, the second contact pair, and the third contact pair.

[0223] Based on the loads applied to the inner ring by the first contact pair, the second contact pair, and the third contact pair, a mechanical equilibrium analysis is performed on the inner ring to obtain the axial displacement, radial displacement, and angular displacement of the inner ring.

[0224] Based on the axial, radial, and angular displacements of the inner ring, the loads borne by the main push roller and the auxiliary push roller are calculated respectively.

[0225] In one possible design, the calculation module 123 is further configured to calculate the mutual approach amount of the first contact pair based on structural parameters and material parameters using a first formula; wherein the first formula is:

[0226]

[0227] in, It is the mutual approach quantity of the first contact pair, D pw1 It is the distribution circle diameter of the main pusher roller, θ is the angular displacement, and δ a It is the axial displacement, P ais the axial clearance, m is the number of main push rollers, and i is the i-th roller out of the m rollers. It is the position distribution angle of the i-th roller;

[0228] Based on structural and material parameters, the mutual approach between the inner and outer raceways at the second contact pair is calculated using a second formula; whereby the second formula is:

[0229]

[0230] in, D is the mutual approach amount between the inner and outer raceways at the second contact pair. w2 It is the nominal diameter of the auxiliary push roller; In the position distribution angle The distance between the inner and outer raceways after the auxiliary push roller bears the load;

[0231]

[0232] Where, δ r It is the radial displacement, D pw2 It is the diameter of the distribution circle of the auxiliary push roller;

[0233] A0 = D w +0.5P a sina

[0234] Where A0 is the normal distance between the inner and outer raceways before the auxiliary push roller is loaded; at the second contact pair, the auxiliary push roller with the largest load is used as the reference. This represents the positional distribution angle of the i-th auxiliary push roller, where n is the number of auxiliary push rollers.

[0235] Based on structural and material parameters, the mutual approach between the inner and outer raceways at the third contact pair is calculated using a third formula; whereby the third formula is:

[0236]

[0237] in, It is the amount of approach between the inner and outer raceways at the third contact point. In the position distribution angle The distance between the inner and outer raceways after the auxiliary roller bears the load;

[0238]

[0239] At the third contact pair, the auxiliary thrust roller with the largest load is used as the reference. This represents the position distribution angle of the i-th auxiliary push roller.

[0240] In one possible design, the calculation module 123 is also used to perform a mechanical equilibrium analysis on the inner ring, obtaining the axial displacement, radial displacement, and angular displacement of the inner ring, including:

[0241] Based on the static equilibrium equation of the inner ring in the axial direction, the axial displacement of the inner ring is obtained.

[0242] The static equilibrium equation of the inner ring in the axial direction is:

[0243]

[0244] Among them, F a It is the axial load borne by the inner ring;

[0245] The radial displacement of the inner ring is obtained based on the static equilibrium equation of the inner ring in the radial direction.

[0246] The static equilibrium equation of the inner ring in the radial direction is:

[0247]

[0248] Among them, F r It is the radial load borne by the inner ring;

[0249] The angular displacement of the inner ring is obtained based on the static equilibrium equation of the inner ring in the direction of rotation of the inner ring.

[0250] The static equilibrium equation of the inner ring in the direction of rotation of the inner ring is:

[0251]

[0252] Among them, M k It is the overturning moment load borne by the inner ring, d c It is the distance between the distribution plane of the main push raceway and the distribution plane of the auxiliary push raceway.

[0253] The bearing load distribution calculation device provided in this embodiment can execute a bearing load distribution calculation method of the above embodiment. Its implementation principle and technical effect are similar, and will not be described again in this embodiment.

[0254] In a specific implementation of the aforementioned bearing load distribution calculation method, each module can be implemented as a processor. The processor can execute computer execution instructions stored in the memory, thereby enabling the processor to execute the aforementioned bearing load distribution calculation method.

[0255] Figure 13 This is a schematic diagram of a bearing load distribution calculation device provided in an embodiment of this application. Figure 13As shown, the electronic device 130 includes at least one processor 131 and a memory 132. The electronic device 130 also includes a communication component 133. The processor 131, memory 132, and communication component 133 are connected via a bus 134.

[0256] In the specific implementation process, at least one processor 131 executes the computer execution instructions stored in the memory 132, causing at least one processor 131 to execute the bearing load distribution calculation method of claims 5-8 as executed on the bearing load distribution calculation device side as described above.

[0257] The specific implementation process of processor 131 can be found in the above method embodiments, and its implementation principle and technical effect are similar, so it will not be repeated here. In the above embodiments, it should be understood that the processor can be a Central Processing Unit (CPU), or other general-purpose processors, Digital Signal Processors (DSPs), Application Specific Integrated Circuits (ASICs), etc. A general-purpose processor can be a microprocessor or any conventional processor. The steps of the method disclosed in this invention can be directly manifested as execution by a hardware processor, or execution by a combination of hardware and software modules within the processor.

[0258] The memory may include high-speed RAM, and may also include non-volatile storage (NVM), such as at least one disk storage.

[0259] The bus can be an Industry Standard Architecture (ISA bus), a Peripheral Component Interconnect (PCI bus), or an Extended Industry Standard Architecture (EISA bus), etc. Buses can be categorized as address buses, data buses, control buses, etc. For ease of illustration, the buses shown in the accompanying drawings are not limited to a single bus or a single type of bus.

[0260] The above description of the functions implemented by the bearing load distribution calculation device and the main control device illustrates the solution provided by the embodiments of the present invention. It is understood that, in order to achieve the above functions, the bearing load distribution calculation device or the main control device includes hardware structures and / or software modules corresponding to the execution of each function. By combining the units and algorithm steps of the various examples described in the embodiments of the present invention, the embodiments of the present invention can be implemented in hardware or a combination of hardware and computer software. Whether a function is executed by hardware or by computer software driving hardware depends on the specific application and design constraints of the technical solution. Those skilled in the art can use different methods to implement the described functions for each specific application, but such implementation should not be considered beyond the scope of the technical solution of the embodiments of the present invention.

[0261] This application also provides a computer-readable storage medium storing computer-executable instructions, which, when executed by a processor, are used to implement the bearing load distribution calculation method described above.

[0262] The aforementioned readable storage medium can be implemented by any type of volatile or non-volatile storage device or a combination thereof, such as static random access memory (SRAM), electrically erasable programmable read-only memory (EEPROM), erasable programmable read-only memory (EPROM), programmable read-only memory (PROM), read-only memory (ROM), magnetic storage, flash memory, magnetic disk, or optical disk. The readable storage medium can be any available medium accessible to a general-purpose or special-purpose computer.

[0263] An exemplary readable storage medium is coupled to a processor, enabling the processor to read information from and write information to the readable storage medium. Of course, the readable storage medium can also be a component of the processor. The processor and the readable storage medium can reside in an Application Specific Integrated Circuit (ASIC). Alternatively, the processor and the readable storage medium can exist as discrete components in an electronic device or a host device.

[0264] This application also provides a computer program product, including a computer program stored in a readable storage medium, wherein at least one processor of an electronic device can read the computer program from the readable storage medium, and the at least one processor executes the computer program to cause the electronic device to perform the scheme provided in any of the above embodiments.

[0265] Those skilled in the art will understand that all or part of the steps of the above method embodiments can be implemented by hardware related to program instructions. The aforementioned program can be stored in a computer-readable storage medium. When the program is executed, it performs the steps of the above method embodiments; and the aforementioned storage medium includes various media capable of storing program code, such as ROM, RAM, magnetic disk, or optical disk.

[0266] The technical solutions of this application have been described above with reference to the preferred embodiments shown in the accompanying drawings. However, it is readily understood by those skilled in the art that the scope of protection of this application is obviously not limited to these specific embodiments. The above embodiments are only used to illustrate the technical solutions of this application and are not intended to limit them. Although this application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features therein. These modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of this application.

Claims

1. A composite bearing, characterized in that, include: First outer ring, second outer ring, inner ring, main push roller, main push cage, auxiliary push roller and auxiliary push cage; The first outer ring and the second outer ring are fastened together to form a whole outer ring and are fitted onto the inner ring; The upper inner wall of the first outer ring and the upper outer wall of the inner ring are spaced apart to form a main push raceway. The main push roller is installed in the main push raceway through the main push retainer. The main push roller is a cylindrical roller. The contact between the main push roller and the main push raceway is a line contact. An auxiliary pusher raceway is formed between the lower inner wall of the first outer ring, the inner wall of the second outer ring, and the lower outer wall of the inner ring. The auxiliary pusher roller is installed in the auxiliary pusher raceway through the auxiliary pusher retainer. The auxiliary pusher roller is a cross cylindrical roller. The contact form between the auxiliary pusher roller and the auxiliary pusher raceway is a line contact. Both the lower inner wall of the first outer ring and the inner wall of the second outer ring are provided with chamfers, and the two chamfers are spaced apart to form a first right-angled groove rolling surface; The lower side of the outer wall of the inner ring is provided with a second right-angle groove rolling surface, and the first right-angle groove rolling surface and the second right-angle groove rolling surface are spaced apart to form the auxiliary push track; The main pusher roller forms line contact with the first outer ring and the inner ring respectively, generating two first contact lines; the two first contact lines form a first contact pair, which is used to bear radial load and overturning moment; The auxiliary pusher roller forms line contact with the upper half of the first outer ring raceway and the lower half of the inner ring raceway, respectively, and generates two second contact lines. The two second contact lines form a second contact pair, which is used to bear radial load and overturning moment. The auxiliary pusher roller forms line contact with the lower half of the second outer ring raceway and the upper half of the inner ring raceway, respectively, and generates two third contact lines. The two third contact lines form a third contact pair, which is used to bear radial load and overturning moment. As the inner ring floats relative to the first outer ring in the radial direction of the inner ring, the mutual approach of the first contact pair and the second contact pair also fluctuates accordingly. As the inner ring floats relative to the second outer ring in the radial direction of the inner ring, the mutual approach of the third contact pair also floats accordingly.

2. A method for calculating bearing load distribution, characterized in that, The method is applied to a calculation unit used to calculate the bearing load of the combined bearing as described in claim 1, wherein the combined bearing includes: a first outer ring, a second outer ring, an inner ring, a main thrust roller, and an auxiliary thrust roller. The structural parameters, material parameters, and load parameters of the combined bearing are collected, and an external load is applied to the combined bearing based on the load parameters; Based on the structural parameters and the material parameters, the mutual approach of the first contact pair, the second contact pair, and the third contact pair is calculated respectively; wherein, the first contact pair is generated by the line contact formed between the main push roller and the first outer ring and the inner ring respectively, the second contact pair is generated by the line contact formed between the upper half raceway of the first outer ring and the lower half raceway of the inner ring respectively, and the third contact pair is generated by the line contact formed between the lower half raceway of the second outer ring and the upper half raceway of the inner ring respectively, and the first contact pair, the second contact pair, and the third contact pair are all used to bear radial loads and overturning moments; Based on the mutual approach of the first contact pair, the second contact pair, and the third contact pair, the loads borne by the main push roller and the auxiliary push roller are calculated respectively.

3. The method according to claim 2, characterized in that, The calculation of the loads borne by the main push roller and the auxiliary push roller based on the mutual approach of the first contact pair, the second contact pair, and the third contact pair includes: Based on the mutual approach of the first contact pair, the second contact pair, and the third contact pair, the loads acting on the inner ring by the first contact pair, the second contact pair, and the third contact pair are calculated respectively. Based on the loads applied to the inner ring by the first contact pair, the second contact pair, and the third contact pair, a mechanical equilibrium analysis is performed on the inner ring to obtain the axial displacement, radial displacement, and angular displacement of the inner ring. Based on the axial displacement, radial displacement, and angular displacement of the inner ring, the loads borne by the main push roller and the auxiliary push roller are calculated respectively.

4. A bearing load distribution calculation system, characterized in that, include: A combined bearing and a calculation unit as described in claim 1, wherein the calculation unit is used to execute the bearing load distribution calculation method as described in any one of claims 2 to 3 of the load distribution calculation system.

5. A bearing load distribution calculation device, characterized in that, The device is applied to a computing unit, which is used to calculate the bearing load of a combined bearing as described in claim 1, wherein the combined bearing includes: a first outer ring, a second outer ring, an inner ring, a main thrust roller, and an auxiliary thrust roller, and the device includes: an acquisition module, a processing module, and a calculation module. The acquisition module is used to acquire the structural parameters, material parameters, and load parameters of the combined bearing; The processing module is used to apply an external load to the combined bearing based on the load parameters; The calculation module is used to calculate the mutual approach of the first contact pair, the second contact pair, and the third contact pair based on the structural parameters and the material parameters, respectively; wherein, the first contact pair is generated by the line contact formed between the main push roller and the first outer ring and the inner ring, respectively; the second contact pair is generated by the line contact formed between the first outer ring and the inner ring, respectively; and the third contact pair is generated by the line contact formed between the second outer ring and the inner ring, respectively. The first contact pair, the second contact pair, and the third contact pair are all used to bear radial loads and overturning moments. The calculation module is also used to calculate the load borne by the main push roller and the auxiliary push roller respectively based on the mutual approach of the first contact pair, the second contact pair and the third contact pair.

6. An electronic device, characterized in that, include: A processor, and a memory communicatively connected to the processor; The memory stores computer-executed instructions; When the processor executes the computer execution instructions stored in the memory, it is used to implement the bearing load distribution calculation method as described in any one of claims 2 to 3.

7. A computer-readable storage medium, characterized in that, The computer-readable storage medium stores computer-executable instructions, which, when executed by a processor, are used to implement the bearing load distribution calculation method as described in any one of claims 2 to 3.

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