Main bearing of heading machine and load distribution calculation method and system thereof

Abstract

The application discloses a main bearing of a heading machine and a load distribution calculation method and system thereof, which is characterized in that: a first outer ring and a second outer ring are connected to form a whole outer ring, which is sleeved on an inner ring, only two rows of raceways are formed between the whole outer ring and the inner ring, cylindrical rolling elements are arranged on a main pushing raceway, and ball rolling elements are arranged on an auxiliary pushing raceway, the main pushing roller is in linear contact with the main pushing raceway, and the auxiliary pushing roller is in point contact with the auxiliary pushing raceway, so that a ball-cylinder combined rotary disc bearing structure in a point-linear mixed contact form is formed, and the load borne by the radial roller and the auxiliary pushing roller is relatively small compared with the main pushing roller in the main bearing structure of the heading machine, therefore, the auxiliary pushing roller can bear axial load, radial load and overturning moment load at the same time through the point contact form between the ball rolling elements and the auxiliary pushing raceway, and it is not necessary to separately arrange a row of radial rollers and corresponding raceways, so that the structure of the main bearing of the heading machine is greatly simplified under the premise of ensuring bearing reliability.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of heading machine, in particular, relates to a kind of heading machine main bearing, in addition, it further relates to the load distribution calculation method and system of the above-mentioned heading machine main bearing. BACKGROUND

[0002] Heading machine is a kind of engineering machinery for tunnel excavation, integrates machine, electricity, liquid and information technology, can carry out long distance, high depth, large diameter tunnel excavation work, and can adapt to harsh working environment, working process automation, intelligent, high working efficiency, and no manual intervention, greatly reduce the work burden of construction personnel. In the process of tunnel excavation, main bearing has very important role, needs to bear the axial load, radial load and overturning moment of soil or rock applied to cutterhead in the process of heading. The existing heading machine main bearing is generally three rows of cylindrical roller bearings, including one inner ring, two outer rings, three rows of cylindrical rollers and cage, wherein, main push roller bears axial load and overturning moment, auxiliary push roller bears overturning moment, radial roller bears radial load alone, and the overall structure is relatively complex. In addition, the load distribution method of existing main bearing is only suitable for point or line single contact form of rotary disc bearing, and cannot be applied to point, line mixed contact form load distribution calculation. SUMMARY

[0003] The present application provides a kind of heading machine main bearing and its load distribution calculation method and system, to solve the technical problem of complex structure of three rows of cylindrical roller bearing structure adopted by existing heading machine main bearing.

[0004] According to one aspect of the present application, a kind of heading machine main bearing is provided, including first outer ring, auxiliary push roller, second outer ring, main push cage, main push roller, inner ring and auxiliary push cage, the first outer ring and second outer ring are fixedly connected as a whole outer ring and are set on the inner ring, the first outer ring and the inner ring form main push raceway, the second outer ring and the inner ring form auxiliary push raceway, the main push roller is installed in main push raceway by main push cage, the auxiliary push roller is installed in auxiliary push raceway by auxiliary push cage, the main push roller is cylindrical roller, its contact form with main push raceway is line contact, for bearing axial load and overturning moment, the auxiliary push roller is spherical roller, its contact form with auxiliary push raceway is point contact, for bearing axial load, radial load and overturning moment.

[0005] Further, the main push roller forms linear contact with the first outer ring and the inner ring respectively, two contact lines form a first contact pair, the bottom end inner wall of the first outer ring is provided with a first arc surface, the top end inner wall of the second outer ring is provided with a second arc surface, the outer side wall of the inner ring is provided with a third arc surface and a fourth arc surface, the first arc surface is oppositely arranged with the third arc surface, and the second arc surface is oppositely arranged with the fourth arc surface, the four arc surfaces are equi-arc design and symmetrically distributed, the auxiliary push roller is in point contact with the first arc surface and the third arc surface, two contact points form a second contact pair, and the auxiliary push roller is also in point contact with the second arc surface and the fourth arc surface, and two contact points form a third contact pair.

[0006] In addition, the application also provides a load distribution calculation method of a main bearing of a heading machine, which is used for calculating the load distribution of the main bearing of the heading machine and comprises the following contents:

[0007] Obtaining the geometric parameters, material parameters and load parameters of the main bearing;

[0008] Applying external load to the main bearing of the heading machine based on the load parameters, and calculating the deformation amount of the main push roller and the auxiliary push roller based on the geometric parameters and the material parameters after the load is applied;

[0009] Calculating the load of the main push roller and the auxiliary push roller acting on the inner ring based on the calculation results of the deformation amount of the main push roller and the auxiliary push roller;

[0010] Performing mechanical balance analysis on the inner ring based on the calculation results of the load of the main push roller and the auxiliary push roller acting on the inner ring, obtaining the axial displacement amount, the radial displacement amount and the angular displacement amount of the inner ring, and calculating the load borne by each main push roller and auxiliary push roller.

[0011] Further, the deformation amount of the main push roller is calculated based on the following formula:

[0012]

[0013] Wherein, represents the deformation amount of the i th main push roller, D pw1 represents the distribution circle diameter of the main push roller, δ a represents the axial displacement amount of the inner ring, P a represents the axial clearance, and θ represents the angular displacement amount of the inner ring, represents the position distribution angle of the i th main push roller, m represents the number of main push rollers.

[0014] Further, the deformation amount of the auxiliary push roller includes the deformation amount generated by the second contact pair and the third contact pair, wherein the deformation amount generated by the second contact pair is calculated based on the following formula:

[0015]

[0016] wherein, represents the deformation amount generated by the second contact pair of the i-th auxiliary thrust roller, A0represents the distance between the curvature centers of the inner and outer ring grooves when the auxiliary thrust roller is in full contact with the auxiliary raceway and the contact deformation is 0, represents the groove curvature center distance of the second contact pair at the position distribution angle of the i-th auxiliary thrust roller after the auxiliary thrust roller is loaded, n represents the number of auxiliary thrust rollers;

[0017] The deformation amount generated by the third contact pair is calculated based on the following formula:

[0018]

[0019] wherein, represents the deformation amount generated by the third contact pair of the i-th auxiliary thrust roller, represents the groove curvature center distance of the third contact pair at the position distribution angle of the i-th auxiliary thrust roller after the auxiliary thrust roller is loaded.

[0020] Further, the load acting on the inner ring by the main thrust roller is calculated based on the following formula:

[0021]

[0022] wherein, represents the load acting on the inner ring by the i-th main thrust roller, K m represents the linear contact elastic deformation constant of the main thrust roller.

[0023] Further, the load acting on the inner ring by the second contact pair of the auxiliary thrust roller is calculated based on the following formula:

[0024]

[0025] wherein, represents the load acting on the inner ring by the second contact pair of the i-th auxiliary thrust roller, K s represents the linear contact elastic deformation constant of the auxiliary thrust roller;

[0026] The load acting on the inner ring by the third contact pair of the auxiliary thrust roller is calculated based on the following formula:

[0027]

[0028] wherein, represents the load acting on the inner ring by the third contact pair of the i-th auxiliary thrust roller.

[0029] Further, the process of the mechanical equilibrium analysis of the inner ring is specifically as follows:

[0030] The contact angles of the second contact pair and the third contact pair of each auxiliary pushing roller are respectively updated and calculated;

[0031] Based on the updated contact angles, static equilibrium equations are constructed in the axial direction, the radial direction and the rotation direction of the inner ring, so as to construct a static equilibrium equation group;

[0032] The static equilibrium equation group is solved by using the quasi-Newton method, so as to obtain the axial displacement, the radial displacement and the angular displacement of the inner ring.

[0033] Further, the static equilibrium equation in the axial direction is as follows:

[0034]

[0035] The static equilibrium equation in the radial direction is as follows:

[0036]

[0037] The static equilibrium equation in the rotation direction of the inner ring is as follows:

[0038]

[0039] Wherein, F a , F r and M k respectively represent the axial load, the radial load and the overturning moment load, m and n respectively represent the number of the main pushing rollers and the auxiliary pushing rollers, represents the load of the i th main pushing roller acting on the inner ring, and respectively represent the load of the second contact pair and the third contact pair of the i th auxiliary pushing roller acting on the inner ring, and respectively represent the contact angles of the second contact pair and the third contact pair of the i th auxiliary pushing roller at the distribution angle after the bearing is loaded, represents the position distribution angle of the i th auxiliary pushing roller, D pw1 and D pw2 respectively represent the distribution circle diameters of the main pushing rollers and the auxiliary pushing rollers, represents the position distribution angle of the i th main pushing roller, d c represents the distance between the distribution planes of the main pushing raceway and the auxiliary pushing raceway.

[0040] In addition, the present application also provides a load distribution calculation system of a main bearing of a heading machine, which is used for calculating the load distribution of the main bearing of the heading machine as described above, and comprises:

[0041] A parameter acquisition module is configured to acquire geometric parameters, material parameters, and load parameters of the main bearing;

[0042] A deformation calculation module is configured to apply external load to the main bearing of the heading machine based on the load parameters, and calculate deformations of the main thrust rollers and the auxiliary thrust rollers based on the geometric parameters and the material parameters after the load is applied;

[0043] A load calculation module is configured to calculate loads of the main thrust rollers and the auxiliary thrust rollers acting on the inner ring based on the deformation calculation results of the main thrust rollers and the auxiliary thrust rollers.

[0044] A balance analysis module is configured to perform mechanical balance analysis on the inner ring based on the load calculation results of the main thrust rollers and the auxiliary thrust rollers acting on the inner ring, to obtain axial displacement, radial displacement, and angular displacement of the inner ring, and to calculate loads borne by each of the main thrust rollers and the auxiliary thrust rollers.

[0045] The present application has the following effects:

[0046] The main bearing of the heading machine is provided with the first outer ring and the second outer ring connected as a whole outer ring above and below, and the whole outer ring is sleeved on the inner ring to form two rows of raceways between the whole outer ring and the inner ring, the cylindrical rolling elements are arranged on the main thrust raceway, and the spherical rolling elements are arranged on the auxiliary thrust raceway, the main thrust rollers are in linear contact with the main thrust raceway, and the auxiliary thrust rollers are in point contact with the auxiliary thrust raceway, thereby forming a spherical-cylindrical combined rotary disc bearing structure in a point-linear mixed contact form, the cylindrical rolling elements bear the axial load and the overturning moment load, and the spherical rolling elements bear the axial load, the radial load, and the overturning moment load at the same time, and since the radial rollers and the auxiliary thrust rollers bear relatively small loads compared with the main thrust rollers in the main bearing structure of the heading machine, the auxiliary thrust rollers can bear the axial load, the radial load, and the overturning moment load at the same time through the point contact form between the spherical rolling elements and the auxiliary thrust raceway, and it is not necessary to separately arrange a row of radial rollers and corresponding raceways, thereby greatly simplifying the structure of the main bearing of the heading machine under the premise of ensuring load bearing reliability.

[0047] In addition, the load distribution calculation method of the main bearing of the heading machine is provided with the following steps: after the geometric parameters, the material parameters, and the load parameters of the main bearing are acquired, external load is applied to the main bearing of the heading machine based on the acquired load parameters, deformations of the main thrust rollers and the auxiliary thrust rollers after the main bearing bears the load are calculated, loads of the main thrust rollers and the auxiliary thrust rollers acting on the inner ring are calculated, mechanical balance analysis is performed on the inner ring to obtain axial displacement, radial displacement, and angular displacement of the inner ring, and loads borne by each of the main thrust rollers and the auxiliary thrust rollers are calculated, thereby obtaining the load distribution results of the main bearing, and therefore, the present application provides a brand-new load distribution calculation method suitable for the point-linear mixed contact form, and the load distribution of the spherical-cylindrical combined rotary disc bearing structure in the point-linear mixed contact form can be analyzed.

[0048] In addition, the load distribution calculation system of the main bearing of the heading machine also has the above-mentioned advantages.

[0049] In addition to the above-mentioned purposes, features and advantages, the present application has other purposes, features and advantages. The present application will be further described below with reference to the drawings. BRIEF DESCRIPTION OF DRAWINGS

[0050] The drawings constituting a part of this application are used to provide further understanding of the present application, the schematic embodiments of the present application and the description thereof are used to explain the present application, and do not constitute improper limitation on the present application. In the drawings:

[0051] Figure 1 is a structural schematic diagram of the main bearing of the heading machine of the preferred embodiment of the present application.

[0052] Figure 2 is a structural schematic diagram of the auxiliary thrust retainer of the preferred embodiment of the present application.

[0053] Figure 3 is a structural schematic diagram of the main bearing of the heading machine of the preferred embodiment of the present application.

[0054] Figure 4 is a flowchart of the load distribution calculation method of the main bearing of the heading machine of another embodiment of the present application.

[0055] Figure 5 is a schematic diagram of the displacement of the curvature center of the inner ring groove of the bearing after the bearing is loaded in another embodiment of the present application.

[0056] Figure 6 is a schematic diagram of the load distribution of the rolling element at the first contact pair of the main bearing of the heading machine calculated in another embodiment of the present application.

[0057] Figure 7 is a schematic diagram of the load distribution of the rolling element at the second contact pair of the main bearing of the heading machine calculated in another embodiment of the present application.

[0058] Figure 8 is a schematic diagram of the load distribution of the rolling element at the third contact pair of the main bearing of the heading machine calculated in another embodiment of the present application.

[0059] Figure 9 is a schematic diagram of the module structure of the load distribution calculation system of the main bearing of the heading machine of another embodiment of the present application.

[0060] BRIEF DESCRIPTION OF DRAWINGS

[0061] 1, first outer ring; 2, auxiliary thrust roller; 3, second outer ring; 4, main thrust retainer; 5, main thrust roller; 6, inner ring; 7, auxiliary thrust retainer. DETAILED DESCRIPTION

[0062] The embodiments of the present application will be described in detail below with reference to the accompanying drawings, but the present application can be implemented in various different ways as defined and covered by the following description.

[0063] It can be understood that, as shown in the preferred embodiment of the present application, a main bearing of a heading machine is provided, which comprises a first outer ring 1, an auxiliary push roller 2, a second outer ring 3, a main push retainer 4, a main push roller 5, an inner ring 6 and an auxiliary push retainer 7, the first outer ring 1 and the second outer ring 3 are fixedly connected as a whole outer ring and are sleeved on the inner ring 6, and a rolling track is formed between the inner wall of the whole outer ring and the outer wall of the inner ring 6, wherein the main push rolling track is formed between the first outer ring 1 and the inner ring 6, and the auxiliary push rolling track is formed between the second outer ring 3 and the inner ring 6. The main push roller 5 is installed in the main push rolling track through the main push retainer 4, and the plurality of main push rollers 5 are distributed and arranged through the isolation of the main push retainer 4. The auxiliary push roller 2 is installed in the auxiliary push rolling track through the auxiliary push retainer 7, and the plurality of auxiliary push rollers 2 are distributed and arranged through the isolation of the auxiliary push retainer 7. Among them, the main push roller 5 is a cylindrical roller, and when the bearing bears a load, the contact form between the main push roller 5 and the main push rolling track is linear contact, which is used to bear the axial load and the overturning moment. The auxiliary push roller 2 is a ball roller, and the contact form between the auxiliary push roller 2 and the auxiliary push rolling track is point contact, which is used to bear the axial load, the radial load and the overturning moment. Figures 1 to 3 Specifically, the main push roller 5 forms linear contact with the first outer ring 1 and the inner ring 6 respectively, and the two contact lines form a first contact pair. The bottom end inner wall of the first outer ring 1 is provided with a first circular arc surface, the top end inner wall of the second outer ring 3 is provided with a second circular arc surface, and the outer side wall of the inner ring 6 is provided with a third circular arc surface and a fourth circular arc surface. The first circular arc surface is oppositely arranged with the third circular arc surface, and the second circular arc surface is oppositely arranged with the fourth circular arc surface. The four circular arc surfaces are designed as equal arcs and are symmetrically distributed. The auxiliary push roller 2 forms point contact with the first circular arc surface and the third circular arc surface, and the two contact points form a second contact pair. The auxiliary push roller 2 also forms point contact with the second circular arc surface and the fourth circular arc surface, and the two contact points form a third contact pair. It can be understood that there are two contact pairs between the auxiliary push roller and the auxiliary push rolling track, and there are four contact points, which improves the carrying capacity of the auxiliary push rolling track.

[0064]

[0065] ​It can be understood that the main bearing of the tunneling machine in the embodiment is sleeved on the inner ring 6 by connecting the first outer ring 1 and the second outer ring 3 into a whole outer ring, only forming two rows of raceways between the whole outer ring and the inner ring 6, arranging the cylindrical rolling elements on the main thrust raceway and the ball rolling elements on the auxiliary thrust raceway, and the main thrust roller 5 being in line contact with the main thrust raceway and the auxiliary thrust roller 2 being in point contact with the auxiliary thrust raceway, so as to form a ball-cylinder combined rotary bearing structure in a point-line mixed contact form. The cylindrical rolling elements bear the axial load and the overturning moment load, and the ball rolling elements bear the axial load, the radial load and the overturning moment load at the same time. Since the load borne by the radial roller and the auxiliary thrust roller is relatively small compared with the main thrust roller 5 in the main bearing structure of the tunneling machine, the auxiliary thrust roller can bear the axial load, the radial load and the overturning moment load at the same time through the point contact form between the ball rolling elements and the auxiliary thrust raceway, and it is not necessary to separately arrange a row of radial rollers and the corresponding raceway. The structure of the main bearing of the tunneling machine is greatly simplified under the premise of ensuring the reliability of bearing.

[0066] In addition, in combination with Figures 3 to 5 Another embodiment of the present application further provides a load distribution calculation method of the main bearing of the tunneling machine, which is used for calculating the load distribution of the main bearing of the tunneling machine as described above, and includes the following contents.

[0067] Step S1: obtaining the geometric parameters, material parameters and load parameters of the main bearing;

[0068] Step S2: applying external load to the main bearing of the tunneling machine based on the load parameters, and calculating the deformation amounts of the main thrust rollers and the auxiliary thrust rollers based on the geometric parameters and the material parameters after the load is applied;

[0069] Step S3: calculating the loads of the main thrust rollers and the auxiliary thrust rollers acting on the inner ring based on the calculation results of the deformation amounts of the main thrust rollers and the auxiliary thrust rollers;

[0070] Step S4: performing mechanical balance analysis on the inner ring based on the calculation results of the loads of the main thrust rollers and the auxiliary thrust rollers acting on the inner ring, obtaining the axial displacement amount, the radial displacement amount and the angular displacement amount of the inner ring, and calculating the loads borne by each main thrust roller and auxiliary thrust roller.

[0071] It can be understood that the load distribution calculation method of the main bearing of the tunneling machine in the embodiment, after obtaining the geometric parameters, material parameters and load parameters of the main bearing, first applies external load to the main bearing based on the obtained load parameters, then calculates the deformation amount of the main thrust roller and the auxiliary thrust roller after the main bearing is subjected to load, then respectively calculates the load of the main thrust roller and the auxiliary thrust roller acting on the inner ring, finally performs mechanical balance analysis on the inner ring to obtain the axial displacement amount, the radial displacement amount and the angular displacement amount of the inner ring, so as to calculate the load borne by each main thrust roller and auxiliary thrust roller, and then obtain the load distribution result of the main bearing. Therefore, the application proposes a brand-new load distribution calculation method suitable for point-line mixed contact form, which can perform load distribution analysis on the ball-cylinder combined rotary bearing structure with point-line mixed contact form.

[0072] It can be understood that in the step S1, the geometric parameters specifically include the distribution circle diameter D pw1 of the main thrust cylindrical roller, the distribution circle diameter D pw2 of the auxiliary thrust ball roller, the nominal diameter D w1 of the main thrust cylindrical roller, the effective length L we1 of the main thrust cylindrical roller, the diameter D w2 of the auxiliary thrust ball roller, the distance d c between the distribution planes of the main thrust raceway and the auxiliary thrust raceway, the initial contact angle α0 of the auxiliary thrust roller, the curvature radius coefficient f e of the auxiliary outer raceway groove, the curvature radius coefficient f i of the auxiliary inner raceway groove, the radial clearance P r , the number m of the main thrust cylindrical rollers, the number n of the auxiliary thrust ball rollers and the like. The material parameters include the elastic modulus E1 of the raceway material, the elastic modulus E2 of the roller material, the Poisson's ratio v1 of the raceway material and the Poisson's ratio v2 of the roller material. The load parameters include the axial load F a , the radial load F r and the overturning moment load M k borne by the bearing inner ring.

[0073] It can be understood that in the step S2, the axial load F a , the radial load F r and the overturning moment load M k obtained in the step S1 are applied to the main bearing, and then the deformation amounts of the main thrust roller and the auxiliary thrust roller are calculated. Specifically, the main thrust roller of the combined bearing only bears the axial load F a and the overturning moment load M k , and the deformation amount of the main thrust roller is calculated based on the following formula:

[0074]

[0075] wherein, denotes the deformation of the i-th main thrust roller, D pw1 denotes the distribution circle diameter of the main thrust roller, δ a denotes the axial displacement of the inner ring, θ denotes the angular displacement of the inner ring, P a denotes the axial clearance, P a = P r tan α0, denotes the position distribution angle of the i-th main thrust roller, with the roller under the greatest load as the reference, i = 1, 2, …, m, m denotes the number of main thrust rollers. Wherein, the axial displacement δ a and the angular displacement θ of the inner ring are unknown quantities, and the rest are known quantities.

[0076] In addition, the auxiliary thrust rollers of the combined bearing simultaneously bear the axial load F a , the radial load F r , and the overturning moment load M k , and the deformation of the auxiliary thrust roller specifically includes the deformation caused by the second contact pair and the third contact pair. The deformation caused by the second contact pair can be calculated based on the following formula:

[0077]

[0078] Wherein, denotes the deformation of the second contact pair of the i-th auxiliary thrust roller, A0denotes the distance between the curvature centers of the inner and outer ring raceways when the auxiliary thrust roller is in complete contact with the auxiliary raceway and the contact deformation is 0, denotes the position distribution angle of the i-th auxiliary thrust roller after the auxiliary thrust roller is loaded , with the curvature center distance of the second contact pair at the position, with the roller under the greatest load as the reference, i = 1, 2, …, n, n denotes the number of auxiliary thrust rollers. Wherein, A0= (f i +f e -1)D w2 , A denotes the distance between the curvature centers of the inner and outer ring raceways before the bearing is loaded, A = (f i +f e -1)D w2 -P r cos α0, R i denotes the radius of the circle on which the inner raceway curvature center is located, δ r denotes the radial displacement of the inner ring. Wherein, the axial displacement δ a , the angular displacement θ, and the radial displacement δ r of the inner ring are unknown quantities, and the rest are known quantities.

[0079] Similarly, the deformation amount generated by the third contact pair of the i-th auxiliary pushing roller is calculated based on the following formula:

[0080]

[0081] wherein, represents the deformation amount generated by the third contact pair of the i-th auxiliary pushing roller, represents the groove curvature center distance of the third contact pair at the position distribution angle of the i-th auxiliary pushing roller after the auxiliary pushing roller is loaded.

[0082] It can be understood that in the step S3, the load of the inner ring acted by the main pushing roller is calculated based on the following formula:

[0083]

[0084] wherein, represents the load of the inner ring acted by the i-th main pushing roller, K m represents the linear contact elastic deformation constant of the main pushing roller,

[0085] In addition, the load of the inner ring acted by the second contact pair of the auxiliary pushing roller is calculated based on the following formula:

[0086]

[0087] wherein, represents the load of the inner ring acted by the i-th auxiliary pushing roller, K s represents the linear contact elastic deformation constant of the auxiliary pushing roller, and ∑ρ ie respectively represent the curvature of the contact point between the auxiliary pushing roller and the inner and outer raceway and the function, and respectively represent the curvature of the auxiliary pushing roller and the function related to the coefficient of the inner and outer raceway at the i-th contact point.

[0088] In addition, the load of the inner ring acted by the third contact pair of the auxiliary pushing roller is calculated based on the following formula:

[0089]

[0090] wherein, represents the load of the inner ring acted by the third contact pair of the i-th auxiliary pushing roller.

[0091] It can be understood that in the step S4, the process of the mechanical balance analysis of the inner ring is specifically as follows:

[0092] The contact angle of the second contact pair and the third contact pair of each auxiliary pushing roller is updated and calculated respectively; ​

[0093] Based on the updated contact angles, static equilibrium equations are constructed in the axial direction, the radial direction and the inner ring rotation direction respectively to construct a static equilibrium equation set;

[0094] The static equilibrium equation set is solved by using a quasi-Newton method to obtain the axial displacement amount, the radial displacement amount and the angular displacement amount of the inner ring.

[0095] Specifically, since the bearing is loaded, the inner ring has a relative displacement relative to the outer ring, thereby causing the contact angles of the second contact pair and the third contact pair of the auxiliary push roller to change, and therefore the contact angles of the second contact pair and the third contact pair of each auxiliary push roller need to be updated and calculated respectively, which is specifically calculated based on the following formula:

[0096]

[0097]

[0098]

[0099] Then, the inner ring is subjected to mechanical equilibrium analysis, and static equilibrium equations are listed in the axial direction, the radial direction and the inner ring rotation direction respectively, wherein the static equilibrium equation in the axial direction is:

[0100]

[0101] The static equilibrium equation in the radial direction is:

[0102]

[0103] The static equilibrium equation in the inner ring rotation direction is:

[0104]

[0105] Wherein, F a , F r and M k respectively represent the axial load, the radial load and the overturning moment load, m and n respectively represent the number of the main push roller and the auxiliary push roller, represents the load of the i th main push roller acting on the inner ring, and respectively represent the load of the second contact pair and the third contact pair of the i th auxiliary push roller acting on the inner ring, and respectively represent the contact angles of the second contact pair and the third contact pair of the i th auxiliary push roller at the distribution angle after the bearing is loaded, represents the position distribution angle of the i th auxiliary push roller, D pw1 and D pw2These represent the distribution circle diameters of the main push roller and the auxiliary push roller, respectively. d represents the position distribution angle of the i-th main pusher roller. c This indicates the distance between the distribution planes of the main pusher raceway and the auxiliary pusher raceway.

[0106] Then, the nonlinear equations consisting of equations (10), (11), and (12) are solved using the quasi-Newton method, and the axial displacement δ can be calculated. a Radial displacement δ r And the angular displacement θ. Among them, the quasi-Newton method is an existing algorithm, so the specific solution principle will not be elaborated here.

[0107] Finally, the calculated δ a δ r Substituting θ into formulas (4), (5), and (6), the load borne by each main push roller and auxiliary push roller can be calculated, thus obtaining the load distribution result of the main bearing. It can be understood that in the above bearing distribution calculation process, the influence of the bearing radial clearance and the distance between the distribution surfaces of the main push raceway and the auxiliary push raceway on the bearing load distribution is also considered, which improves the accuracy of the load distribution calculation.

[0108] For example, using the bearing-related parameters in Table 1 to calculate the load distribution, the load distribution of the rolling elements at the first contact pair, second contact pair, and third contact pair in the above-mentioned ball-and-spindle combined slewing bearing structure is as follows: Figures 6 to 8 As shown.

[0109] Table 1. Relevant parameters of the main bearing

[0110]

[0111] In addition, such as Figure 9 As shown, another embodiment of the present invention also provides a load distribution calculation system for a tunneling machine main bearing, used to calculate the load distribution of the tunneling machine main bearing as described above, preferably employing the load distribution calculation method as described above, including:

[0112] The parameter acquisition module is used to acquire the geometric parameters, material parameters, and load parameters of the main bearing.

[0113] The deformation calculation module is used to apply an external load to the main bearing of the tunneling machine based on load parameters, and to calculate the deformation of the main thrust roller and the auxiliary thrust roller based on geometric parameters and material parameters respectively after the load is applied.

[0114] The load calculation module is used to calculate the loads acting on the inner ring by the main push roller and the auxiliary push roller based on the deformation calculation results of the main push roller and the auxiliary push roller, respectively.

[0115] The balance analysis module is used for performing mechanical balance analysis on the inner ring based on the load calculation results of the main thrust roller and the auxiliary thrust roller acting on the inner ring, obtaining the axial displacement, the radial displacement and the angular displacement of the inner ring, and calculating the load borne by each main thrust roller and auxiliary thrust roller.

[0116] It can be understood that the load distribution calculation system of the main bearing of the heading machine in the embodiment, after obtaining the geometric parameters, material parameters and load parameters of the main bearing, first applies external load to the main bearing of the heading machine based on the obtained load parameters, then calculates the deformation of the main thrust roller and the auxiliary thrust roller after the main bearing is subjected to load, respectively calculates the load of the main thrust roller and the auxiliary thrust roller acting on the inner ring, finally performs mechanical balance analysis on the inner ring, obtains the axial displacement, the radial displacement and the angular displacement of the inner ring, and thus calculates the load borne by each main thrust roller and auxiliary thrust roller, and further obtains the load distribution result of the main bearing. Therefore, the application proposes a brand-new load distribution calculation system suitable for point-line mixed contact form, which can perform load distribution analysis on the ball-cylinder combined rotary disc bearing structure with point-line mixed contact form.

[0117] The above only describes the preferred embodiments of the present application and is not used to limit the present application. For those skilled in the art, the present application can have various modifications and changes. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application shall be included in the protection scope of the present application.

[0118] Those skilled in the art will understand that the embodiments of the present application can be provided as a method, a system, or a computer program product. Therefore, the present application can adopt a completely hardware embodiment, a completely software embodiment, or an embodiment combining software and hardware aspects. Moreover, the present application can adopt the form of a computer program product implemented on one or more computer usable storage media containing computer usable program codes (including but not limited to disk memory, CD-ROM, optical memory, etc.). The solutions in the embodiments of the present application can be implemented in various computer languages, such as object-oriented programming language Java and interpreted scripting language JavaScript, etc.

[0119] The present application is described with reference to flowcharts and / or block diagrams according to the methods, devices (systems), and computer program products of the embodiments of the present application. It should be understood that each flow and / or block in the flowcharts and / or block diagrams, and the combination of the flows and / or blocks in the flowcharts and / or block diagrams can be implemented by computer program instructions. These computer program instructions can be provided to the processor of a general-purpose computer, a special-purpose computer, an embedded processor, or other programmable data processing devices to produce a machine, so that the instructions executed by the processor of the computer or other programmable data processing devices produce a machine that implements the flowcharts and / or block diagrams. Figure 1one or more processes and / or blocks Figure 1 an apparatus for performing the functions specified in the flowchart

[0120] These computer program instructions can also be stored in a computer- readable memory that can direct a computer or other programmable data processing apparatus to function in a particular manner, such that the instructions stored in the computer-readable memory produce an article of manufacture including instructions which implement the flowchart Figure 1 one or more processes and / or blocks Figure 1 an apparatus for performing the functions specified in the flowchart

[0121] These computer program instructions can also be loaded onto a computer or other programmable data processing apparatus to cause a series of operational steps to be performed on the computer or other programmable apparatus to produce a computer implemented process such that the instructions which execute on the computer or other programmable apparatus provide steps for implementing the flowchart Figure 1 one or more processes and / or blocks Figure 1 an apparatus for performing the functions specified in the flowchart

[0122] While the preferred embodiments of the application have been described, additional variations and modifications can be made to the embodiments by those skilled in the art once they learn of the basic inventive concepts. Therefore, the appended claims are intended to encompass within their scope all such variations and modifications as are included within the scope of the application.

[0123] Obviously, numerous modifications and variations of the present application are possible in light of the above teachings. It is therefore to be understood that within the scope of the appended claims and their equivalents, the application can be practiced otherwise than as specifically described.

Claims

1. A load distribution calculation method of a main bearing of a heading machine, for calculating a load distribution of a main bearing of a heading machine, wherein, The main bearing of the heading machine comprises a first outer ring (1), an auxiliary push roller (2), a second outer ring (3), a main push retainer (4), a main push roller (5), an inner ring (6) and an auxiliary push retainer (7), the first outer ring (1) and the second outer ring (3) are fixedly connected as a whole outer ring and are sleeved on the inner ring (6), a main push roller way is formed between the first outer ring (1) and the inner ring (6), an auxiliary push roller way is formed between the second outer ring (3) and the inner ring (6), the main push roller (5) is installed in the main push roller way through the main push retainer (4), the auxiliary push roller (2) is installed in the auxiliary push roller way through the auxiliary push retainer (7), the main push roller (5) is a cylindrical roller, the contact form between the main push roller (5) and the main push roller way is linear contact, which is used for bearing axial load and overturning moment, the auxiliary push roller (2) is a ball roller, the contact form between the auxiliary push roller (2) and the auxiliary push roller way is point contact, which is used for bearing axial load, radial load and overturning moment, the main push roller (5) forms linear contact with the first outer ring (1) and the inner ring (6) respectively, and two contact lines form a first contact pair, a first circular arc surface is arranged on the inner wall of the bottom end of the first outer ring (1), a second circular arc surface is arranged on the inner wall of the top end of the second outer ring (3), a third circular arc surface and a fourth circular arc surface are arranged on the outer side wall of the inner ring (6), the first circular arc surface is oppositely arranged with the third circular arc surface, the second circular arc surface is oppositely arranged with the fourth circular arc surface, the four circular arc surfaces are equi-arc design and symmetrically distributed, the auxiliary push roller (2) is in point contact with the first circular arc surface and the third circular arc surface, two contact points form a second contact pair, the auxiliary push roller (2) is also in point contact with the second circular arc surface and the fourth circular arc surface, and two contact points form a third contact pair, and the main bearing is characterized by comprising the following contents: Obtaining the geometric parameters, material parameters and load parameters of the main bearing; Applying external load to the main bearing of the heading machine based on the load parameters, and calculating the deformation amounts of the main push roller and the auxiliary push roller based on the geometric parameters and the material parameters after the load is applied; Calculating the load of the main push roller and the auxiliary push roller acting on the inner ring based on the deformation amount calculation results of the main push roller and the auxiliary push roller; Performing mechanical balance analysis on the inner ring based on the load calculation results of the main push roller and the auxiliary push roller acting on the inner ring, obtaining the axial displacement amount, the radial displacement amount and the angular displacement amount of the inner ring, and calculating the load borne by each main push roller and auxiliary push roller.

2. The load distribution calculation method of a main bearing of a heading machine according to claim 1, characterized in that, The deformation amount of the main push roller is calculated based on the following formula: wherein, represents the deformation amount of the i-th main thrust roller, D pw1 represents the distribution circle diameter of the main thrust roller, δ a represents the axial displacement amount of the inner ring, P a represents the axial play, θ represents the angular displacement amount of the inner ring, represents the position distribution angle of the i-th main thrust roller, i = 1, 2,..., m, m represents the number of the main thrust rollers.

3. The load distribution calculation method of a main bearing of a heading machine according to claim 1, characterized in that, The deformation amount of the auxiliary push roller includes the deformation amounts generated by the second contact pair and the third contact pair, wherein the deformation amount generated by the second contact pair is calculated based on the following formula: wherein, represents the deformation amount generated by the second contact pair of the i-th auxiliary push roller, A0represents the distance between the curvature centers of the inner and outer ring grooves when the auxiliary push roller is in full contact with the auxiliary push raceway and the contact deformation is 0, represents the position distribution angle of the i-th auxiliary push roller after the auxiliary push roller is loaded at the groove curvature center distance of the second contact pair at the position, i = 1, 2, …, n, n represents the number of auxiliary push rollers; The deformation amount generated by the third contact pair is calculated based on the following formula: wherein, represents the amount of deformation generated by the third contact pair of the ith secondary push roller, represents the distance of the center of curvature of the groove of the third contact pair at the position distribution angle of the ith secondary push roller after the secondary push roller is loaded, represents the distance of the center of curvature of the groove of the third contact pair at the position distribution angle of the ith secondary push roller after the secondary push roller is loaded, 4. The load distribution calculation method of a main bearing of a heading machine according to claim 2, characterized in that, The load of the main push roller acting on the inner ring is calculated based on the following formula: wherein, represents the load of the i-th main roller acting on the inner ring, K m represents the linear contact elastic deformation constant of the main roller.

5. The load distribution calculation method of a main bearing of a heading machine according to claim 3, characterized in that, The load of the second contact pair of the auxiliary push roller acting on the inner ring is calculated based on the following formula: wherein, represents the load of the second contact pair of the ith auxiliary pushing roller acting on the inner ring, K s represents the linear contact elastic deformation constant of the auxiliary pushing roller; The load of the third contact pair of the auxiliary push roller acting on the inner ring is calculated based on the following formula: wherein, represents the load of the third contact pair of the i-th auxiliary pushing roller acting on the inner ring.

6. The load distribution calculation method of a main bearing of a heading machine according to Claim 1, characterized in that, The process of performing mechanical balance analysis on the inner ring is specifically as follows: The contact angles of the second contact pair and the third contact pair of each auxiliary push roller are updated and calculated respectively. The static equilibrium equations are constructed in the axial, radial and inner ring rotation directions respectively based on the updated contact angle to construct a static equilibrium equation set; The static equilibrium equation set is solved by using a quasi-Newton method to obtain the axial displacement, radial displacement and angular displacement of the inner ring.

7. The load distribution calculation method of a main bearing of a heading machine according to claim 6, characterized in that, The axial static equilibrium equation is: The radial static equilibrium equation is: The inner ring rotation direction static equilibrium equation is: wherein F a , F r and M k represent the axial load, the radial load and the overturning moment load, respectively, m and n represent the number of the main and auxiliary thrust rollers, respectively, represents the load of the i-th main thrust roller acting on the inner ring, and represent the load of the second and third contact pairs of the i-th auxiliary thrust roller acting on the inner ring, respectively, and represent the contact angles of the second and third contact pairs of the i-th auxiliary thrust roller at the distribution angles after the bearing is loaded, represents the position distribution angle of the i-th auxiliary thrust roller, D pw1 and D pw2 represent the distribution circle diameters of the main and auxiliary thrust rollers, respectively, represents the position distribution angle of the i-th main thrust roller, d c represents the distance between the distribution planes of the main and auxiliary thrust raceways.

8. A load distribution calculation system of a main bearing of a heading machine for calculating a load distribution of a main bearing of a heading machine, wherein, The main bearing of the heading machine comprises a first outer ring (1), an auxiliary push roller (2), a second outer ring (3), a main push retainer (4), a main push roller (5), an inner ring (6) and an auxiliary push retainer (7), the first outer ring (1) and the second outer ring (3) are fixedly connected as a whole outer ring and are sleeved on the inner ring (6), a main push raceway is formed between the first outer ring (1) and the inner ring (6), an auxiliary push raceway is formed between the second outer ring (3) and the inner ring (6), the main push roller (5) is installed in the main push raceway through the main push retainer (4), the auxiliary push roller (2) is installed in the auxiliary push raceway through the auxiliary push retainer (7), the main push roller (5) is a cylindrical roller, the contact form between the main push roller (5) and the main push raceway is linear contact, which is used for bearing axial load and overturning moment, the auxiliary push roller (2) is a ball roller, the contact form between the auxiliary push roller (2) and the auxiliary push raceway is point contact, which is used for bearing axial load, radial load and overturning moment, the main push roller (5) forms linear contact with the first outer ring (1) and the inner ring (6) respectively, and two contact lines form a first contact pair, a first circular arc surface is arranged on the bottom end inner wall of the first outer ring (1), a second circular arc surface is arranged on the top end inner wall of the second outer ring (3), a third circular arc surface and a fourth circular arc surface are arranged on the outer side wall of the inner ring (6), the first circular arc surface is oppositely arranged with the third circular arc surface, the second circular arc surface is oppositely arranged with the fourth circular arc surface, the four circular arc surfaces are equi-arc design and symmetrically distributed, the auxiliary push roller (2) is in point contact with the first circular arc surface and the third circular arc surface, two contact points form a second contact pair, the auxiliary push roller (2) is also in point contact with the second circular arc surface and the fourth circular arc surface, and two contact points form a third contact pair, and the main bearing comprises the following characteristics: The parameter acquisition module is used for acquiring the geometric parameters, material parameters and load parameters of the main bearing; The deformation calculation module is used for applying external loads to the main bearing of the heading machine based on the load parameters, and calculating the deformation of the main push roller and the auxiliary push roller based on the geometric parameters and the material parameters after the loads are applied; The load calculation module is used for calculating the load of the main push roller and the auxiliary push roller acting on the inner ring based on the deformation calculation results of the main push roller and the auxiliary push roller; The balance analysis module is used for performing mechanical balance analysis on the inner ring based on the load calculation results of the main push roller and the auxiliary push roller acting on the inner ring, obtaining the axial displacement, radial displacement and angular displacement of the inner ring, and calculating the load borne by each main push roller and auxiliary push roller.

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