A reliability and sensitivity analysis method for a rotary table

Abstract

The present application proposes a reliability and sensitivity analysis method for a rotary table, which belongs to the technical field of reliability analysis. The rotary table model is simplified, and a parameterized model of the rotary table is established; the simplified rotary table model is subjected to finite element analysis to obtain the working condition with the weakest rigidity under different load conditions; according to the structure and assembly relationship of each component in the rotary table model, the constraint relationship between the structural parameters of each component is set; under the working condition with the weakest rigidity, the structural parameters of each component are taken as random variables, and the random variables are taken as normal distribution as input to establish a limit state function; according to the limit state function, the parameterized model of the rotary table with the constraint relationship is subjected to reliability and sensitivity analysis to obtain the sensitivity of each structural parameter to reliability. The present application improves the reliability and stability of the rotary table, improves the machining accuracy and consistency of the machine tool, and reduces economic losses.

Description

Technical Field

[0001] The invention belongs to the technical field of reliability analysis, and in particular relates to a reliability and sensitivity analysis method of a rotary table. Background Art

[0002] The cradle-type double rotary table is the core functional component of the five-axis machining center, with the advantages of high dynamic response, high precision and high speed. Its main function is to expand the processing range of the workpiece and improve the processing efficiency. The static stiffness of the rotary table plays a key role in the processing accuracy and stability of the whole machine. In recent years, many scholars have applied sensitivity analysis to machine tool research. Existing research has laid the foundation for the mechanical performance analysis and sensitivity analysis of the rotary table, and its basic principles are quite mature. However, in these studies, scholars only focus on the relationship between the thickness dimension of the plate structure and the performance, while ignoring the influence of other geometric dimensions on the performance except the plate thickness dimension. In addition, in the study of multi-component machine tools, scholars did not consider the assembly relationship between the multi-components, and tended to choose geometric variables that are not related to the assembly relationship in the selection of variables; in addition, from the perspective of practical engineering, the structural parameters of each component of the rotary table are random, while in the above research, the structural parameters of each component of the rotary table are considered to be deterministic. Therefore, the above research has certain limitations. Summary of the invention

[0003] In response to the shortcomings of the existing technology, this application proposes a reliability and sensitivity analysis method for a rotary table, which improves the reliability and stability of the rotary table, provides theoretical reference and data value for the research on rotary tables of high-end machine tools, improves machine tool processing accuracy and consistency, and reduces economic losses.

[0004] A reliability and sensitivity analysis method for a rotary table, comprising:

[0005] Simplify the rotary table model and establish a parameterized model of the rotary table;

[0006] Finite element analysis was performed on the simplified rotary table model to obtain the weakest rigidity condition under different load conditions;

[0007] According to the structure and assembly relationship of each component in the rotary table model, set the constraint relationship between the structural parameters of each component;

[0008] Under the working condition with the weakest rigidity, the structural parameters of each component are taken as random variables, and the random variables are taken as normal distribution as input to establish the limit state function;

[0009] According to the limit state function, reliability and sensitivity analysis is performed on the parameterized model of the rotary table with constraint relationships to obtain the sensitivity of each structural parameter to reliability.

[0010] The rotary table model is a cradle-type double rotary table model.

[0011] The structural parameters of the components include: structural parameters of the A-axis housing, structural parameters of the A-axis rotor shaft, structural parameters of the C-axis rotor shaft, structural parameters of the workbench, structural parameters of the swing frame, structural parameters of the core shaft, structural parameters of the brake shaft and structural parameters of the brake pad.

[0012] The constraint relationship between the setting structure parameters includes:

[0013] Set the constraint relationship required for the assembly relationship between parts in the structural parameters;

[0014] Set the constraint relationship required by the internal structure relationship of the part in the structural parameters.

[0015] The constraint relationship required for the assembly relationship between the components in the setting structure parameters includes:

[0016] Set the constraint relationship between the structural parameters of the spindle and the structural parameters of the A-axis housing:

[0017] Set the constraint relationship between the structural parameters of the mandrel and the structural parameters of the A-axis rotor shaft:

[0018] Set the constraint relationship between the structural parameters of the brake shaft and the structural parameters of the A-axis rotor shaft:

[0019] Set the constraint relationship between the structural parameters of the brake module and the structural parameters of the brake pad:

[0020] Set the constraint relationship between the structural parameters of the brake pad and the structural parameters of the brake shaft:

[0021] Set the constraint relationship between the structural parameters of the swing frame and the structural parameters of the mandrel:

[0022] Set the constraint relationship between the structural parameters of the A-axis rotor shaft, the structural parameters of the brake shaft, and the structural parameters of the C-axis rotor shaft.

[0023] The constraint relationship required for the internal structural relationship of the part in setting the structural parameters includes:

[0024] Set the constraint relationship between the structural parameters of the swing frame.

[0025] Under the working condition with the weakest rigidity, the structural parameters of each component are taken as random variables, and the random variables are taken as normal distribution as input to establish the limit state function. The calculation formula is as follows:

[0026] g(X)=L * -L(X)

[0027] Where X is a normally distributed random variable; g(X) is the limit state function; L* is the limit deformation value of the workbench perpendicular to the workbench surface, and L(X) is the deformation response value of the workbench perpendicular to the workbench surface.

[0028] Beneficial effects:

[0029] This application proposes a reliability and sensitivity analysis method for a rotary table, which uses the maximum directional deformation of the rotary table surface under load as a measure of the rigidity of the rotary table system, sets the constraint relationship between the structural parameters according to the structure and assembly relationship of the main components of the rotary table, takes into account the uncertainty of the structural parameters of the main components, and performs reliability sensitivity analysis on the rotary table system to obtain the degree of influence of different structural parameters on the system rigidity reliability. The method of this application improves the reliability and stability of the rotary table, provides theoretical reference and data value for the research on the rotary table of high-end machine tool equipment, improves the machining accuracy and consistency of machine tools, and reduces economic losses. BRIEF DESCRIPTION OF THE DRAWINGS

[0030] Figure 1 Flow chart of the reliability and sensitivity analysis method of the rotary table of the embodiment of the present application;

[0031] Figure 2 The main structure diagram of the cradle-type double rotary workbench of the embodiment of the present application;

[0032] Figure 3 The finite element model of the cradle-type double rotary table of the embodiment of the present application;

[0033] Figure 4 Grid-independent verification results of the embodiment of the present application;

[0034] Figure 5 Mechanical properties analysis results of the embodiments of the present application; (a) local coordinate system of the cradle-type double rotary table, (b) simulation results under different working conditions;

[0035] Figure 6 Schematic diagram of random variables in an embodiment of the present application;

[0036] Figure 7 Sensitivity analysis results of the embodiments of the present application;

[0037] Figure 8 Parameters that have a greater impact on the rigidity of the cradle-type double rotary table system of the embodiment of the present application;

[0038] Among them, a-brake module, b-brake pad, c-brake shaft, d-rotor shaft, eA shaft housing, f-turntable bearing, g-core shaft, h-swing frame, i-workbench. DETAILED DESCRIPTION

[0039] In recent years, many scholars have applied sensitivity analysis to machine tool research. Some scholars have used sensitivity analysis methods to determine the dimensional parameters that have a greater impact on the dynamic and static characteristics of the machine tool bed. Other scholars have established a finite element model of a large machining center workbench and improved the workbench structure based on sensitivity analysis and topology optimization. However, these studies usually only analyze a single component of the machine tool and ignore the interaction between components. In the study of multi-component systems of machine tools, some scholars have applied sensitivity analysis to determine the dimensional parameters in the column and vertical slide that have a greater impact on the stiffness of the machine tool. The machining center was optimized using a method based on response surface modeling and sensitivity analysis.

[0040] However, in these studies, scholars only focused on the relationship between the thickness of the plate structure and its performance, while ignoring the effects of other geometric dimensions on performance except the plate thickness. This is because changes in plate thickness are relatively easy to achieve, and if unique external structures such as circular and annular structures, or other positioning dimensions are considered, changes in one structural dimension will also cause other structures to change, resulting in the inability to establish a stable parameter model in the later stage, and thus the inability to conduct reliability and sensitivity analysis. In addition, in the study of multi-component machine tools, scholars did not consider the assembly relationship between multiple components, and tended to choose geometric variables that were not related to the assembly relationship. In addition, from a practical engineering perspective, the structural parameters of the components of the rotary table are random.

[0041] Therefore, in order to improve the reliability and stability of the rotary table, the uncertainty of the structural parameters of the rotary table is considered and the reliability sensitivity analysis of its system rigidity is carried out.

[0042] Example:

[0043] This embodiment proposes a reliability and sensitivity analysis method for a rotary table. Figure 1 As shown, including:

[0044] Step S1: simplify the rotary table model and establish a parameterized model of the rotary table;

[0045] The reliability and sensitivity analysis method of the rotary table of this embodiment can be applied to various rotary tables. In order to explain the specific implementation steps in more detail, the rotary table model described in this embodiment is a cradle-type double rotary table model, such as Figure 2 shown.

[0046] First, the cradle-type double rotary table model is simplified, and a rotary table parameterized model is established. Combined with the actual working conditions of the rotary table, a rotary table mechanical performance analysis model is established. This embodiment studies the rotary table in the brake clamping state. Before performing finite element analysis, some structures in the rotary table model that have little effect on static analysis are simplified. Then, based on the geometric structure and assembly relationship of each component of the cradle-type double rotary table, the uncertainty input parameters that need to be analyzed for reliability sensitivity are determined, and then a rotary table parameterized model is established.

[0047] Combined with the actual working conditions of the rotary table, the boundary conditions, contact, material parameters and iteration tolerance of the finite element model are set. Figure 3 In order to ensure the accuracy of finite element analysis, it is necessary to verify the mesh independence of the simulation results. Figure 4 In order to verify the mesh independence of different A-axis angles under the no-load state of the turntable, the number of meshes is selected to be 55894, taking into account the calculation time and calculation accuracy.

[0048] Step S2: Perform finite element analysis on the simplified rotary table model to obtain the weakest rigidity condition under different load conditions;

[0049] The double rotary table in this embodiment can carry a maximum of 600kg workpiece, and the A axis can rotate at ±120°. In order to fully consider the influence of load gravity on the mechanical properties of the rotary table, a square workpiece is taken as an example, and different load conditions are simulated by adjusting the volume of the workpiece and the A axis rotation angle. Figure 5 (a) shows the local coordinate system, and the maximum Z-direction deformation of the worktable surface under load is taken as the output response. The simulation results are shown in Figure 5 (b) as shown.

[0050] Depend on Figure 5 (b) It can be seen that when the A-axis rotation angle is 70° and no load is applied, the maximum deformation of the worktable in the Z direction is 0.01264mm; this result shows that under this working condition, the rigidity of the system is the weakest. According to the principle of the short plate effect, the reliability sensitivity analysis of the rotary table will be carried out under this working condition to study the influence of various geometric structure parameters on the rigidity reliability of the rotary table system.

[0051] Step S3: according to the structure and assembly relationship of each component in the rotary table model, setting the constraint relationship between the structural parameters of each component;

[0052] In general, the structural parameters only include the thickness of the plate. In addition to the plate thickness, this application also includes other geometric structural parameters. In order to more comprehensively measure the impact of various structural parameters on the system reliability, without affecting the overall structural dimensions and assembly relationship of the rotary table, some structural parameters of the main components such as the workbench, swing frame, brake shaft, core shaft, A-axis housing, rotor shaft (including: A-axis rotor shaft, C-axis rotor shaft), brake pads, etc. are regarded as random variables in the analysis process, and the rotary table is regarded as a system. Random variables such as Figure 6 As shown, this embodiment provides 58 variables, among which A1-A4 represent the structural parameters of the A-axis housing (two), B1-B7 represent the structural parameters of the core shaft (two), C1-C7 represent the structural parameters of the A-axis rotor shaft (two), D1-D5 represent the structural parameters of the brake shaft (three), E1-E2 represent the structural parameters of the C-axis rotor shaft, F1-F5 represent the structural parameters of the workbench, G1-G6 represent the structural parameters of the brake pad (three), H1-H2 represent the structural parameters of the brake module, I1-I 20 Represents the structural parameters of the swing frame.

[0053] The turntable structure, assembly process, etc. will have certain restrictions on the structural parameters of each component. Therefore, the structural parameters should be limited within the allowable conditions to make the results conform to the actual engineering.

[0054] In order to satisfy the assembly relationship of each component, the following constraints are imposed:

[0055] The constraint relationship between the setting structure parameters includes:

[0056] Set the constraint relationship required for the assembly relationship between parts in the structural parameters;

[0057] Set the constraint relationship required by the internal structure relationship of the part in the structural parameters.

[0058] The constraint relationship required for the assembly relationship between the components in the setting structure parameters includes:

[0059] Set the constraint relationship between the structural parameters of the spindle and the structural parameters of the A-axis housing:

[0060] Set the constraint relationship between the structural parameters of the mandrel and the structural parameters of the A-axis rotor shaft:

[0061] Set the constraint relationship between the structural parameters of the brake shaft and the structural parameters of the A-axis rotor shaft:

[0062] Set the constraint relationship between the structural parameters of the brake module and the structural parameters of the brake pad:

[0063] Set the constraint relationship between the structural parameters of the brake pad and the structural parameters of the brake shaft:

[0064] Set the constraint relationship between the structural parameters of the A-axis rotor shaft, the structural parameters of the brake shaft, and the structural parameters of the C-axis rotor shaft;

[0065] Set the constraint relationship between the structural parameters of the swing frame and the structural parameters of the mandrel:

[0066] The constraint relationship required for the internal structural relationship of the part in setting the structural parameters includes:

[0067] Set the constraint relationship between the structural parameters of the swing frame.

[0068] The structural parameters of each component are taken as random variables. Table 1 shows the physical meaning of each random variable:

[0069] Table 1 Meaning of random variables

[0070]

[0071]

[0072] In this embodiment, the specific constraint relationship is set as follows:

[0073] Constraint 1: Set the constraint relationship between the outer diameter of the mandrel and the thickness of the A-axis shell (that is, set the constraint relationship between the structural parameters of the mandrel and the structural parameters of the A-axis shell);

[0074] In the actual rotary table, the outer diameter of the mandrel is 2mm smaller than the outer diameter of the A-axis shell, and the inner diameter of the mandrel is 485mm, so the outer diameter of the mandrel B3 and the thickness of the A-axis shell A3 meet the following conditions:

[0075] B3=(A3+242.5)×2-2 (1)

[0076] Constraint 2: Set the constraint relationship between the flange height of the A-axis rotor shaft and the flange height of the core shaft (that is, set the constraint relationship between the structural parameters of the core shaft and the structural parameters of the A-axis rotor shaft);

[0077] In order to meet the assembly requirements, the A-axis rotor shaft flange height C1 and the core shaft flange height B2 meet the following requirements:

[0078] C1=B2-1 (2)

[0079] Constraint 3: Set the constraint relationship between the outer height of the brake shaft and the structural parameters of the A-axis rotor shaft that matches the brake shaft (i.e., set the constraint relationship between the structural parameters of the brake shaft and the structural parameters of the A-axis rotor shaft); the outer height D4 of the brake shaft and the outer boss height C6 of the A-axis rotor shaft that matches it satisfy:

[0080] D4=C6+1 (3)

[0081] Constraint 4: Set the constraint relationship between the brake shaft ring width 2 and the outer boss ring width of the A-axis rotor shaft (that is, set the constraint relationship between the structural parameters of the brake shaft and the structural parameters of the A-axis rotor shaft);

[0082] The chamber between the A-axis rotor shaft and the A-axis housing is equipped with a motor (not shown in the figure). In order to ensure the motor installation requirements, the structural parameters of the chamber are not set as variables; at the same time, the brake shaft and the brake module cannot interfere with each other, so the sum of the brake shaft ring width 2D5 and the A-axis rotor shaft outer boss ring width C7 should remain unchanged:

[0083] D5=62.5-C7 (4)

[0084] Constraint 5: Set the constraint relationship between the thickness of the inner cavity of the brake module, the diameter of the inner cavity of the brake module, the outer diameter of the brake pad, and the thickness of the brake pad (that is, set the constraint relationship between the structural parameters of the brake module and the structural parameters of the brake pad);

[0085] This example studies the clamping state of the turntable, so the brake module is simplified to simulate the brake clamping state. G5 represents the outer diameter of the brake pad, G6 represents 1 / 2 of the outer thickness of the brake pad, H1 represents the thickness of the inner cavity of the brake module, and its value is equal to the thickness of the brake pad. H2 represents the diameter of the inner cavity of the brake module, and its value is 2mm larger than the outer diameter of the brake pad. Therefore, the structural parameters H1 and H2 of the brake module and the structural parameters G5 and G6 of the brake pad satisfy:

[0086] H1=G6 (5)

[0087] H2=G5+2 (6)

[0088] Constraint 6: Set the constraint relationship between the inner thickness of the brake pad and the boss thickness on the outer edge of the brake shaft (i.e., set the constraint relationship between the structural parameters of the brake pad and the structural parameters of the brake shaft);

[0089] G1 represents 1 / 2 of the inner thickness of the brake pad, and D1 represents the boss thickness on the outer edge of the brake shaft. In order to ensure that the brake shaft does not interfere with the brake module, the sum of G1 and D1 should remain unchanged:

[0090] G1=10-D1 (7)

[0091] Constraint 7: Set the constraint relationship between the height of the outer boss of the A-axis rotor shaft, the ring width of the outer boss of the A-axis rotor shaft, the height of the outer boss of the C-axis rotor shaft, and the ring width of the outer boss of the C-axis rotor shaft (that is, set the constraint relationship between the structural parameters of the A-axis rotor shaft, the structural parameters of the brake shaft, and the structural parameters of the C-axis rotor shaft).

[0092] The C-axis rotor shaft matches the brake shaft, so:

[0093] E1=C6+1 (8)

[0094] E2=C7 (9)

[0095] Among them, C6 is the height of the outer boss of the A-axis rotor shaft, C7 is the ring width of the outer boss of the A-axis rotor shaft, E1 is the height of the outer boss of the C-axis rotor shaft, and E2 is the ring width of the outer boss of the C-axis rotor shaft.

[0096] Constraint 8: Set the constraint relationship between the total length of the swing frame and the thickness of the outer edge of the mandrel and the height of the mandrel boss (that is, set the constraint relationship between the structural parameters of the swing frame and the structural parameters of the mandrel);

[0097] Because the turntable is installed on the machine bed, the distance between the outer sides of the left and right A-axis housings should remain unchanged during the size change of the turntable components. In this example, the length of the A-axis housing is not set variable, so the distance between the two spindles should remain unchanged, so the total length of the swing frame I 17 The structural parameters B4 and B5 of the mandrel meet the following requirements:

[0098] I 17 =2×(640-B4-B5) (10)

[0099] Constraint 9: Set the constraint relationship between the outer edge ring width of the swing frame and the ring width of the middle boss of the mandrel (that is, set the constraint relationship between the structural parameters of the swing frame and the structural parameters of the mandrel); the outer edge ring width of the swing frame I 13 The width B6 of the middle boss ring of the mandrel meets the following requirements:

[0100] I 13 =B6 (11)

[0101] Constraint 10: Set the constraint relationship between the inner diameter of the mandrel, the thickness of the outer edge of the mandrel and the inner diameter of the outer edge of the swing frame (that is, set the constraint relationship between the structural parameters of the swing frame and the structural parameters of the mandrel);

[0102] B1 represents the inner diameter of the mandrel, B7 represents the width of the boss ring on the outer edge of the mandrel, and I represents the inner diameter of the outer edge of the swing frame. 12 Cooperate with the mandrel to meet the following requirements:

[0103] I 12 =B1+B7×2 (12)

[0104] The constraint relationship required for the internal structural relationship of the part in setting the structural parameters includes:

[0105] Constraint 11: Set the constraint relationship between the structural parameters of the swing frame.

[0106] In order to meet the structural requirements of the parts, the following constraints should be met, namely, the shell thickness on both sides of the swing frame is I8, the outer edge thickness of the swing frame is I 14And the total length of the rack I 17 Require:

[0107] I 14 =I 17 -565+I8 (13)

[0108] Step S4: Under the working condition with the weakest rigidity, the structural parameters of each component are taken as random variables, and the random variables are taken as normal distribution as input to establish the limit state function;

[0109] After setting constraints on the turntable structural parameters, some parameters become dependent variables (such as B3, C1, D4, D5, E1, E2, G1, H1, H2, I 12 ,I 13 ,I 14 ,I 17 , these 13 all become dependent variables), the final structural parameters and means are shown in Table 2. In this embodiment, the mean of each variable is the center position of the normal distribution, and each variable randomly takes a value in the determined normal distribution. The system uncertainty structural parameters are constructed as the input of the limit state function. The system uncertainty structural parameters are X=[A1,…,B1,…,C1,…,D1,…,E1,…,F1,…,G1,…,H1,…,I1,…] T ;

[0110] Table 2 Structural parameters and average values ​​of rotary table

[0111]

[0112]

[0113] Under extreme working conditions, considering the influence of uncertain factors, the limit state function is established based on whether the maximum Z-direction deformation of the workbench exceeds the allowable value:

[0114] Under the working condition with the weakest rigidity, the structural parameters of each component are taken as random variables, and the random variables are taken as normal distribution as input to establish the limit state function. The calculation formula is as follows:

[0115] g(X)=L * -L(X)

[0116] Where, X=[A1,…,B1,…,C1,…,D1,…,E1,…,F1,…,G1,…,H1,…,I1,…] T is a normally distributed random variable, g(X) is a limit state function; this embodiment establishes Figure 5(a), where the Z axis represents the direction perpendicular to the worktable surface, L* is the maximum Z-axis deformation allowed by the rotary table, and L(X) is the Z-axis deformation response value of the table. L(X)<0 indicates that the table system is in a failed state; L(X)>0 indicates that the rotary table system is in a reliable state; L(X)=0 indicates that the rotary table system is in a limit state.

[0117] Step S5: According to the limit state function, reliability and sensitivity analysis is performed on the parameterized model of the rotary table with constraint relationships to obtain the sensitivity of each structural parameter to reliability.

[0118] The reliability sensitivity analysis of the rotary table system was carried out using the 6 Sigma analysis module in the workbench. The initial sample set was obtained using Latin hypercube sampling. The response surface type was Kriging. The table structure parameters were all selected to be truncated normal distribution with a coefficient of variation of 0.02. The sensitivity analysis results are shown in the figure. Figure 7 The results show that the structural parameters of the swing frame have the greatest impact on the reliability of the rotary table system, while the structural parameters of the table have less impact on the reliability of the rotary table system.

[0119] According to the sensitivity analysis results, the ten structural parameters that have the greatest impact on the rigidity of the turntable system are extracted, such as Figure 8 As shown in the figure, in the process of designing and optimizing rotary work, the following parameters with high sensitivity should be focused on. The simulation results show that the simulation results provide theoretical reference and data value for the research of rotary tables of high-end machine tools, which can improve the machining accuracy and consistency of machine tools and reduce economic losses.

[0120] The various embodiments in the present application are described in a progressive manner, and the same or similar parts between the various embodiments can be referenced to each other, and each embodiment focuses on the differences from other embodiments.

[0121] The protection scope of the present application is not limited to the above-mentioned embodiments. Obviously, those skilled in the art can make various changes and modifications to the present disclosure without departing from the scope and spirit of the present disclosure. If these changes and modifications fall within the scope of the claims of the present disclosure and their equivalents, the intention of the present disclosure also includes these changes and modifications.

Claims

1. A reliability and sensitivity analysis method for a rotary table, characterized in that: include: Simplify the rotary table model and establish a parameterized model of the rotary table; Finite element analysis was performed on the simplified rotary table model to obtain the weakest rigidity condition under different load conditions; According to the structure and assembly relationship of each component in the rotary table model, set the constraint relationship between the structural parameters of each component; Under the working condition with the weakest rigidity, the structural parameters of each component are taken as random variables, and the random variables are taken as normal distribution as input to establish the limit state function; According to the limit state function, reliability and sensitivity analysis is performed on the parameterized model of the rotary table with constraint relationships to obtain the sensitivity of each structural parameter to the reliability of the rotary table; The rotary table model is a cradle-type double rotary table model; the structural parameters of the components include: the structural parameters of the A-axis housing, the structural parameters of the A-axis rotor shaft, the structural parameters of the C-axis rotor shaft, the structural parameters of the table, the structural parameters of the swing frame, the structural parameters of the spindle, the structural parameters of the brake shaft and the structural parameters of the brake pad; Under the condition with the weakest rigidity, the structural parameters of each component are taken as random variables, and the random variables are taken as normal distribution as input to establish the limit state function. The calculation formula is as follows: g(X)=L*-L(X) Where X is a normally distributed random variable, g(X) is the limit state function, L* is the limit deformation value of the workbench perpendicular to the workbench surface, and L(X) is the deformation response value of the workbench in the direction perpendicular to the workbench surface.

2. The reliability and sensitivity analysis method of a rotary table according to claim 1, characterized in that: The setting of the constraint relationship between the structural parameters of each component includes: Set the constraint relationship required for the assembly relationship between parts in the structural parameters; Set the constraint relationship required by the internal structure relationship of the part in the structural parameters.

3. The reliability and sensitivity analysis method of a rotary table according to claim 2, characterized in that: The constraint relationship required for the assembly relationship between the components in the setting structure parameters includes: Set the constraint relationship between the structural parameters of the spindle and the structural parameters of the A-axis housing: Set the constraint relationship between the structural parameters of the mandrel and the structural parameters of the A-axis rotor shaft: Set the constraint relationship between the structural parameters of the brake shaft and the structural parameters of the A-axis rotor shaft: Set the constraint relationship between the structural parameters of the brake module and the structural parameters of the brake pad: Set the constraint relationship between the structural parameters of the brake pad and the structural parameters of the brake shaft: Set the constraint relationship between the structural parameters of the swing frame and the structural parameters of the mandrel: Set the constraint relationship between the structural parameters of the A-axis rotor shaft, the structural parameters of the brake shaft, and the structural parameters of the C-axis rotor shaft.

4. The reliability and sensitivity analysis method of a rotary table according to claim 2, characterized in that: The constraint relationship required for the internal structural relationship of the part in setting the structural parameters includes: Set the constraint relationship between the structural parameters of the swing frame.

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