A vertical machining center beam structure design method and beam structure

Abstract

The present invention discloses a method for designing a beam structure of a vertical machining center, which belongs to the field of machine tools and includes the following steps: establishing a finite element analysis model of the beam; setting the contact type between the main components according to the connection relationship between the parts; setting boundary conditions for the finite element analysis model of the beam; optimizing the side guide rail mounting surface of the beam to obtain a preliminary optimization model of the beam; and impact simulating the upper guide rail mounting surface of the preliminary optimization model of the beam to obtain a final optimization model of the beam. In the present application, the static and dynamic performances of the optimized beam structure are improved, the force arm between the X-axis load and the side guide rail is reduced, the wear on one side of the guide rail is reduced, the service life of the guide rail is extended, and the overall structure is lighter, which reduces the difficulty of processing and adjustment, and is conducive to the stable output of the motor force of the entire axis. The present application also relates to a beam structure designed according to the above-mentioned method for designing a beam structure of a vertical machining center.

Description

Technical Field

[0001] The invention relates to the field of machine tools, and in particular to a method for designing a crossbeam structure of a vertical machining center and a crossbeam structure designed according to the method for designing a crossbeam structure of a vertical machining center. Background Art

[0002] In the field of machine tools, linear motors are generally used to drive the saddle and slider in the crossbeam structure of the vertical machining center. The guide rails are set on the same side of the crossbeam end face, and the saddle is generally mounted vertically or tilted at 45 degrees. The vertical wall-mounted method easily causes the center of the X-axis drive component to deviate from the X-axis guide rail, resulting in a large lateral force arm and a large radial torque on the crossbeam side guide rail, which can easily cause damage to the guide rail. The 45-degree tilted style will cause the overall volume and weight of the crossbeam structure to be larger, heavier, and more deformed. It is also difficult to process, install, and debug, which will eventually affect the output stability of the linear motor force, thereby reducing the accuracy of the entire axis. Summary of the invention

[0003] In order to overcome the shortcomings of the prior art, one of the objects of the present invention is to provide a method for designing the crossbeam structure of a vertical machining center, by first performing static analysis and preliminary optimization on the guide rail mounting surface on the crossbeam, and then performing impact simulation on the guide rail mounting surface on the crossbeam, to obtain the final optimized model of the crossbeam and verify its feasibility, thereby reducing the force arm between the X-axis load and the guide rail, reducing the wear on one side of the guide rail, and making the overall structure lighter, reducing its processing difficulty and adjustment difficulty, which is conducive to the stable output of the motor force of the entire axis.

[0004] In order to overcome the deficiencies of the prior art, a second object of the present invention is to provide a vertical machining center beam structure that reduces wear on one side of the guide rail and has a lighter overall structure, thereby reducing the difficulty of machining and adjusting the structure.

[0005] One of the purposes of the present invention is achieved by the following technical solution:

[0006] A method for designing a beam structure of a vertical machining center comprises the following steps:

[0007] S1. Establish a finite element analysis model of the beam;

[0008] S2. Setting the contact type between the main components according to the connection relationship between the parts;

[0009] S3. Setting boundary conditions for the finite element analysis model of the beam: firstly, meshing the finite element analysis model of the beam is performed, and then load forces are applied to the guide rail mounting surface and the side guide rail mounting surface of the beam respectively, and full constraints are set on the connection surface between the beam and the column;

[0010] S4. Create a list of deformation point positions Y of the side rail mounting surface of the beam model in the Z direction 1 ~Y n And record the corresponding deformation L 1 ~L n , if the deformation L exceeds the preset range, the corresponding deformation point position is the first dangerous point position;

[0011] S5. Establish a strain gauge sensor at the first dangerous point, calculate the static stress and natural frequency of the saddle structure at the first dangerous point, analyze and calculate the strength and dynamic response of the side guide rail mounting surface of the beam structure, so as to obtain the simulated strain of the side guide rail mounting surface of the beam;

[0012] S6, calculating the correlation between the simulated strain and the real strain of the side guide rail mounting surface of the beam, changing the height of the side guide rail mounting surface in the beam model, and repeating steps S4-S5 to obtain a preliminary optimization model of the beam;

[0013] S7. Establish the list of deformation point positions of the guide rail mounting surface in the Z direction on the preliminary optimization model of the beam X 1 ~X n And record the corresponding deformation H 1 ~H n , if the deformation amount H exceeds the preset range, the corresponding deformation point position is the second dangerous point position;

[0014] S8, applying a vertical downward impact initial velocity to the concentrated mass point of the preliminary optimization model of the beam to perform impact simulation, and obtaining the failure mode and energy absorption ratio at each second dangerous point of the beam structure, wherein the concentrated mass point is the center of gravity of the beam structure, the failure mode includes progressive failure, bending, and breaking, and the energy absorption ratio is 30% to 90%;

[0015] S9, integrating and weighting the data at each dangerous point of the beam structure, comprehensively evaluating the beam model, changing the width of the upper guide rail installation surface, and repeating steps S7-S8 to obtain the final optimized model of the beam.

[0016] S10. Verify the feasibility of the final optimized model of the beam.

[0017] Furthermore, in the step S3, the upper guide rail mounting surface has a bearing weight of 2×10 4 kg, the load force set on the upper guide rail mounting surface is 2×10 5 N, the load force set on the side rail mounting surface is 3×10 4 N.

[0018] Further, in the step S4, the first dangerous point position is the front end point position, the middle point position, and the rear end point position of the side guide rail mounting surface, the maximum deformation point position is the middle point position, and the maximum deformation amount is 0.03 mm.

[0019] Furthermore, in the step S6, the height of the side guide rail mounting surface is increased by 10 to 15 mm.

[0020] Further, in the step S7, the second dangerous point position is the front end point position, the middle point position, and the rear end point position of the upper guide rail mounting surface, the maximum deformation point position is the middle point position, and the maximum deformation amount is 0.02 mm.

[0021] Furthermore, the S10 step is specifically as follows: performing modal analysis on the final optimized model of the beam, if the maximum deformation of the beam in the Z direction decreases and the difference with the maximum deformation before optimization is within a preset range, the optimization ends; if the maximum deformation of the beam in the Z direction decreases and the difference with the maximum deformation before optimization is not within the preset range or the maximum deformation of the beam in the Z direction increases, the model is corrected and optimized again.

[0022] Furthermore, in the step S1, the crossbeam and the column are connected by bolts, the saddle and the slider are connected by bolts, the upper guide rail and the crossbeam are connected by bolts, the side guide rail and the crossbeam are connected by bolts, the upper guide rail and the slider are clearance-fitted, and the side guide rail and the slider are clearance-fitted.

[0023] Further, in the S2 step, the contact type between the crossbeam and the column is binding contact, the contact type between the saddle and the slider is binding contact, the contact type between the upper guide rail and the crossbeam is binding contact, the contact type between the side guide rail and the crossbeam is binding contact, the contact type between the upper guide rail and the slider is non-separation contact, and the contact type between the side guide rail and the slider is non-separation contact.

[0024] The second object of the present invention is achieved by adopting the following technical solution:

[0025] A beam structure designed according to any one of the above-mentioned methods for designing a beam structure for a vertical machining center, comprising a motor, a saddle, a beam, an upper guide rail, a side guide rail, and two sliders, wherein the upper guide rail is arranged on the upper end surface of the beam, the side guide rail is arranged on the side end surface of the beam, the length directions of the upper guide rail and the side guide rail are parallel to the length direction of the beam, the mounting surface of the upper guide rail is perpendicular to the mounting surface of the side guide rail, the two sliders are arranged on the saddle, and are slidably connected to the upper guide rail and the side guide rail respectively, the motor is arranged between the saddle and the beam, and the motor drives the saddle and the slider to move along the length direction of the beam.

[0026] Furthermore, the cross-section of the saddle is L-shaped.

[0027] Compared with the prior art, the design method of the crossbeam structure of the vertical machining center of the present invention comprises the following steps: S1, establishing a crossbeam finite element analysis model; S2, setting the contact type between the main components according to the connection relationship between the parts; S3, setting boundary conditions for the crossbeam finite element analysis model; S4, establishing a list Y of deformation point positions of the side guide rail mounting surface of the crossbeam model in the Z direction. 1 ~Y n And record the corresponding deformation L 1 ~L n , if the deformation L exceeds the preset range, the corresponding deformation point position is the first dangerous point position; S5, establish a strain gauge sensor at the first dangerous point position, calculate the static stress and natural frequency of the saddle structure at the first dangerous point position, analyze and calculate the strength and dynamic response of the side guide rail mounting surface of the beam structure, so as to obtain the simulated strain of the side guide rail mounting surface of the beam;

[0028] S6, calculate the correlation between the simulated strain and the real strain of the side guide rail mounting surface of the beam, change the height of the side guide rail mounting surface in the beam model, and repeat steps S4-S5 to obtain a preliminary optimization model of the beam; S7, establish a list of deformation point positions of the guide rail mounting surface in the Z direction on the preliminary optimization model of the beam 1 ~X n And record the corresponding deformation H 1 ~H n, if the deformation H exceeds the preset range, the corresponding deformation point position is the second dangerous point position; S8, apply the vertical downward initial impact velocity to the concentrated mass point of the preliminary optimization model of the beam to perform impact simulation, and obtain the failure mode and energy absorption ratio at each second dangerous point position of the beam structure. The concentrated mass point is the center of gravity of the beam structure. The failure mode includes progressive failure, bending, and breaking, and the energy absorption ratio is 30% to 90%; S9, integrate and weight the data at each dangerous point position of the beam structure, conduct a comprehensive evaluation of the beam model, change the width of the upper guide rail mounting surface, and repeat steps S7-S8 to obtain the final optimization model of the beam; S10, verify the feasibility of the final optimization model of the beam, the static and dynamic performances of the optimized beam structure are improved, the force arm between the X-axis load and the side guide rail is reduced, the wear on one side of the guide rail is reduced, the service life of the guide rail is extended, and the overall structure is lighter, which reduces its processing difficulty and adjustment difficulty, which is conducive to the stable output of the motor force of the entire axis. BRIEF DESCRIPTION OF THE DRAWINGS

[0029] Figure 1 It is a flow chart of the method for designing the crossbeam structure of a vertical machining center of the present invention;

[0030] Figure 2 The schematic diagram of the structure of the beam structure designed by the vertical machining center beam structure design method of the present invention is shown in FIG.

[0031] In the figure: 10, motor; 20, crossbeam; 30, saddle; 31, vertical part; 32, horizontal part; 40, upper guide rail; 50, side guide rail; 60, slider. DETAILED DESCRIPTION

[0032] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0033] It should be noted that when a component is referred to as being "fixed to" another component, it may be directly on the other component or there may be another intermediate component through which it is fixed. When a component is considered to be "connected to" another component, it may be directly connected to the other component or there may be another intermediate component at the same time. When a component is considered to be "set on" another component, it may be directly set on the other component or there may be another intermediate component at the same time. The terms "vertical", "horizontal", "left", "right" and similar expressions used herein are for illustrative purposes only.

[0034] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as those commonly understood by those skilled in the art of the present invention. The terms used herein in the specification of the present invention are only for the purpose of describing specific embodiments and are not intended to limit the present invention. The term "and / or" used herein includes any and all combinations of one or more related listed items.

[0035] Figure 2 The beam structure designed for the beam structure design method of the vertical machining center of the present invention includes a motor 10, a beam 20, a saddle 30, an upper guide rail 40, a side guide rail 50, and two sliders 60. The upper guide rail 40 is arranged on the upper end surface of the beam 20, and the side guide rail 50 is arranged on the side end surface of the beam 20. The length directions of the upper guide rail 40 and the side guide rail 50 are parallel to the length direction of the beam 20. The mounting surface of the upper guide rail 40 is perpendicular to the mounting surface of the side guide rail 50. The two sliders 60 are arranged on the saddle 30 and are slidably connected to the upper guide rail 40 and the side guide rail 50 respectively. The motor 10 is arranged between the saddle 30 and the beam 20, and the motor 10 drives the saddle 30 and the slider 60 to move along the length direction of the beam 20. In this embodiment, the crossbeam 20 and the column are connected by bolts, the saddle 30 and the slider 60 are connected by bolts, the upper guide rail 40 and the crossbeam 20 are connected by bolts, the side guide rail 50 and the crossbeam 20 are connected by bolts, the upper guide rail 40 and the corresponding slider 60 are clearance-fitted, and the side guide rail 50 and the corresponding slider 60 are clearance-fitted.

[0036] like Figure 1 As shown, the present application provides a method for designing a beam structure of a vertical machining center, comprising the following steps:

[0037] S1. Establish a finite element analysis model of the beam;

[0038] S2. Setting the contact type between the main components according to the connection relationship between the parts;

[0039] S3. Setting boundary conditions for the finite element analysis model of the beam: firstly meshing the finite element analysis model of the beam, then applying load forces to the mounting surfaces of the upper guide rail 40 and the side guide rail 50 of the beam 20, respectively, and setting full constraints on the connection surface between the beam 20 and the column;

[0040] S4. Create a list Y of deformation point positions of the side guide rail 50 mounting surface of the beam model in the Z direction 1 ~Y n And record the corresponding deformation L 1 ~L n , if the deformation L exceeds the preset range, the corresponding deformation point position is the first dangerous point position;

[0041] S5. Establish a strain gauge sensor at the first danger point, calculate the static stress and natural frequency of the saddle structure at the first danger point, analyze and calculate the strength and dynamic response of the mounting surface of the side guide rail 50 of the beam structure, and obtain the simulated strain of the mounting surface of the side guide rail 50 of the beam;

[0042] S6, calculating the correlation between the simulated strain and the real strain of the mounting surface of the side guide rail 50 of the beam, changing the height of the mounting surface of the side guide rail 50 in the beam model, and repeating steps S4-S5 to obtain a preliminary optimized model of the beam;

[0043] S7. Establish the list of deformation point positions of the guide rail 40 mounting surface in the Z direction on the preliminary optimization model of the crossbeam X 1 ~X n And record the corresponding deformation H 1 ~H n , if the deformation amount H exceeds the preset range, the corresponding deformation point position is the second dangerous point position;

[0044] S8. Apply an initial vertical downward impact velocity to the concentrated mass point of the preliminary optimization model of the beam to perform impact simulation, and obtain the failure mode and energy absorption ratio at each second dangerous point of the beam structure. The concentrated mass point is the center of gravity of the beam structure. The failure mode includes progressive failure, bending, and breaking, and the energy absorption ratio is 30% to 90%;

[0045] S9, integrating and weighting the data at each dangerous point of the beam structure, comprehensively evaluating the beam model, changing the width of the mounting surface of the upper guide rail 40, and repeating steps S7-S8 to obtain the final optimized model of the beam.

[0046] S10. Verify the feasibility of the final optimized model of the beam.

[0047] In step S1, the cross beam 20 is connected to the column by bolts, the saddle 30 is connected to the slider 60 by bolts, the upper guide rail 40 is connected to the cross beam 20 by bolts, the side guide rail 50 is connected to the cross beam 20 by bolts, the upper guide rail 40 and the corresponding slider 60 are clearance matched, and the side guide rail 50 and the corresponding slider 60 are clearance matched. The analysis model is simplified according to the actual assembly relationship of each component, some unnecessary features are removed, and then the simplified model is imported into ANSYS Workbench software for analysis.

[0048] In step S2, the contact type between the crossbeam 20 and the column is set to binding contact, the contact type between the saddle 30 and the slider 60 is set to binding contact, the contact type between the upper guide rail 40 and the crossbeam 20 is set to binding contact, the contact type between the side guide rail 50 and the crossbeam 20 is set to binding contact, the contact type between the upper guide rail 40 and the slider 60 is non-separation contact, and the contact type between the side guide rail 50 and the slider 60 is non-separation contact.

[0049] In step S3, the upper guide rail 40 bears a weight of 2×10 4 kg, the load force set on the upper guide rail 40 mounting surface is 2×10 5 N, the load force set on the mounting surface of the side rail 50 is 3×10 4 N.

[0050] In step S4, the first dangerous point position is the front end point position, the middle point position, and the rear end point position of the installation surface of the side guide rail 50, the maximum deformation point position is the middle point position, and the maximum deformation amount is 0.03 mm.

[0051] In step S5, the calculation formula of the static stress of the saddle structure is: Where F is the magnetic attraction of the saddle assembly to the beam, A is the contact area between the saddle assembly and the beam, M e is the torque, I x is the moment of inertia, l x is the length of the beam; the calculation formula for the natural frequency of the saddle structure is Where, k = EI, where I is the moment of inertia of the saddle section; E is the elastic modulus of the material; m z It is the uniformly distributed mass of the saddle structure.

[0052] In step S6, the height of the mounting surface of the side guide rail 50 is increased by 10 to 15 mm. Specifically, the height of the mounting surface of the side guide rail 50 is increased from the original 20 mm to 30 mm.

[0053] In step S7, the second dangerous point position is the front end point position, the middle point position, and the rear end point position of the installation surface of the upper guide rail 40, the maximum deformation point position is the middle point position, and the maximum deformation amount is 0.02 mm.

[0054] In step S8, the failure mode at the front end point is bending, and the energy absorption ratio is 40%; the failure mode at the middle point is progressive failure, and the energy absorption ratio is 80%; the failure mode at the rear end point is bending, and the energy absorption ratio is 40%.

[0055] In step S9, the width of the mounting surface of the upper guide rail 40 is increased by 5 to 10 mm. Specifically, the width of the mounting surface of the upper guide rail 40 is increased from 20 mm to 25 mm.

[0056] Step S10 is specifically as follows: modal analysis is performed on the final optimized model of the beam. If the maximum deformation of the beam 20 in the Z direction decreases and the difference with the maximum deformation before optimization is within the preset range, the optimization ends; if the maximum deformation of the beam 20 in the Z direction decreases and the difference with the maximum deformation before optimization is not within the preset range or the maximum deformation of the beam 20 in the Z direction increases, the model is corrected and optimized again. In this embodiment, after the beam structure is improved, the maximum deformation of the mounting surface of the side guide rail 50 of the beam 20 in the Z direction is in the middle of the mounting surface of the side guide rail 50, and its value is 0.026mm; the maximum deformation of the mounting surface of the upper guide rail 40 of the beam 20 in the Z direction is in the middle of the mounting surface of the upper guide rail 40, and its value is 0.015mm. The larger value of the maximum deformation is taken, that is, the maximum deformation of the beam 20 in the Z direction is 0.026mm, the maximum equivalent stress is 12MPa, and the first-order frequency of the beam 20 is 179.45Hz. The deformation of the mounting surface of the side guide rail 50 of the beam 20 was reduced by 11%, the deformation of the mounting surface of the upper guide rail 40 was reduced by 33%, the stress was reduced by 38%, and the natural frequency of the first-order mode was increased by 13.7%, meeting the design requirements.

[0057] This application first performs static analysis and preliminary optimization on the mounting surface of the side guide rail 50 of the beam 20 to obtain a preliminary optimized model of the beam; performs impact simulation on the mounting surface of the upper guide rail 40 of the preliminary optimized model of the beam to obtain the final optimized model of the beam, and verifies its feasibility through modal analysis. The static and dynamic performances of the optimized beam structure are improved, the force arm between the X-axis load and the side guide rail 50 is reduced, the wear on one side of the guide rail is reduced, the service life of the guide rail is extended, and the overall structure is lighter, which reduces the difficulty of processing and adjustment, and is conducive to the stable output of the motor force of the entire axis.

[0058] The present application also relates to a beam structure designed according to a beam structure design method for a vertical machining center, comprising a motor 10, a beam 20, a saddle 30, an upper guide rail 40, a side guide rail 50, and two sliders 60. The upper guide rail 40 is arranged on the upper end surface of the beam 20, and the side guide rail 50 is arranged on the side end surface of the beam 20. The length directions of the upper guide rail 40 and the side guide rail 50 are parallel to the length direction of the beam 20. The mounting surface of the upper guide rail 40 is perpendicular to the mounting surface of the side guide rail 50. The two sliders 60 are arranged on the saddle 30 and are slidably connected to the upper guide rail 40 and the side guide rail 50 respectively. The motor 10 is arranged between the saddle 30 and the beam 20, and the motor 10 drives the saddle 30 and the slider 60 to move along the length direction of the beam 20. In this embodiment, the crossbeam 20 and the column are connected by bolts, the saddle 30 and the slider 60 are connected by bolts, the upper guide rail 40 and the crossbeam 20 are connected by bolts, the side guide rail 50 and the crossbeam 20 are connected by bolts, the upper guide rail 40 and the corresponding slider 60 are clearance-fitted, and the side guide rail 50 and the corresponding slider 60 are clearance-fitted.

[0059] In this embodiment, the cross-sectional shape of the saddle 30 is L-shaped. The saddle 30 includes a vertical portion 31 and a horizontal portion 32. The vertical portion 31 is vertically fixedly connected to the horizontal portion 32. Two sliders 60 are respectively arranged on the vertical portion 31 and the horizontal portion 32. The slider 60 at the vertical portion 31 faces the mounting surface of the side guide rail 50, and the slider 60 at the horizontal portion 32 faces the mounting surface of the upper guide rail 40. When in use, the slider 60 at the horizontal portion 32 is used as a side reference to reduce the influence of the magnetic plate suction on the side guide rail 50, and better transfer the magnetic plate suction to the upper guide rail 40, so that the upper guide rail 40 and the crossbeam 20 are not only supported by fixing screws. In a preferred embodiment, the reinforcement ribs on the inner side of the saddle 30 can also be reasonably arranged to effectively resist the suction of the linear motor 10 and the structural deformation caused by gravity, thereby improving the overall accuracy.

[0060] The beam structure designed in the present application can reduce the lever arm of the X-axis load when in use, while reducing the radial damage to the guide rail caused by the driving force of the linear motor 10 and the gravity of the saddle 30, thereby extending the service life of the guide rail. The overall volume and weight of the beam structure are small, and the deformation of the beam is reduced. The processing, installation and debugging are easy, thereby ensuring the output stability of the linear motor 10 force, thereby improving the accuracy of the entire axis.

[0061] The above embodiments only express several implementation methods of the present invention, and the descriptions thereof are relatively specific and detailed, but they cannot be understood as limiting the scope of the invention patent. It should be pointed out that, for ordinary technicians in this field, several modifications and improvements can be made without departing from the concept of the present invention, which are equivalent modifications and improvements made to the above embodiments based on the essential technology of the present invention, and all of them belong to the protection scope of the present invention.

Claims

1. A method for designing a beam structure of a vertical machining center, characterized in that: The following steps are involved: S1. Establish a finite element analysis model of the beam; S2. Setting the contact type between the main components according to the connection relationship between the parts; S3. Setting boundary conditions for the finite element analysis model of the beam: firstly, meshing the finite element analysis model of the beam is performed, and then load forces are applied to the guide rail mounting surface and the side guide rail mounting surface of the beam respectively, and full constraints are set on the connection surface between the beam and the column; S4. Create a list of deformation point positions Y1 to Y2 of the side guide rail mounting surface of the beam model in the Z direction. n And record the corresponding deformation L1~L n , if the deformation L exceeds the preset range, the corresponding deformation point position is the first dangerous point position; S5. Establish a strain gauge sensor at the first dangerous point, calculate the static stress and natural frequency of the saddle structure at the first dangerous point, analyze and calculate the strength and dynamic response of the side guide rail mounting surface of the beam structure, so as to obtain the simulated strain of the side guide rail mounting surface of the beam; S6, calculating the correlation between the simulated strain and the real strain of the side guide rail mounting surface of the beam, changing the height of the side guide rail mounting surface in the beam model, and repeating steps S4-S5 to obtain a preliminary optimization model of the beam; S7, establish the list of deformation point positions X1~X1 on the guide rail mounting surface in the Z direction of the preliminary optimization model of the beam n And record the corresponding deformation H1~H n , if the deformation amount H exceeds the preset range, the corresponding deformation point position is the second dangerous point position; S8, applying a vertical downward impact initial velocity to the concentrated mass point of the preliminary optimization model of the beam to perform impact simulation, and obtaining the failure mode and energy absorption ratio at each second dangerous point of the beam structure, wherein the concentrated mass point is the center of gravity of the beam structure, the failure mode includes progressive failure, bending, and breaking, and the energy absorption ratio is 30% to 90%; S9, integrating and weighting the data at each dangerous point of the beam structure, comprehensively evaluating the beam model, changing the width of the upper guide rail installation surface, and repeating steps S7-S8 to obtain the final optimized model of the beam; S10. Verify the feasibility of the final optimized model of the beam.

2. The method for designing a crossbeam structure of a vertical machining center according to claim 1, characterized in that: In the step S3, the upper guide rail mounting surface has a load bearing capacity of 2×10 4 kg, the load force set on the upper guide rail mounting surface is 2×10 5 N, the load force set on the side rail mounting surface is 3×10 4 N.

3. The method for designing a crossbeam structure of a vertical machining center according to claim 1, characterized in that: In the step S4, the first dangerous point position is the front end point position, the middle point position, and the rear end point position of the side guide rail mounting surface, the maximum deformation point position is the middle point position, and the maximum deformation amount is 0.03 mm.

4. The method for designing a crossbeam structure of a vertical machining center according to claim 1, characterized in that: In the step S6, the height of the side guide rail mounting surface is increased by 10 to 15 mm.

5. The method for designing a beam structure of a vertical machining center according to claim 1, characterized in that: In the step S7, the second dangerous point position is the front end point position, the middle point position, and the rear end point position of the upper guide rail mounting surface, the maximum deformation point position is the middle point position, and the maximum deformation amount is 0.02 mm.

6. The method for designing a beam structure of a vertical machining center according to claim 1, characterized in that: The S10 step is specifically as follows: performing modal analysis on the final optimized model of the beam; if the maximum deformation of the beam in the Z direction decreases and the difference with the maximum deformation before optimization is within a preset range, the optimization ends; if the maximum deformation of the beam in the Z direction decreases and the difference with the maximum deformation before optimization is not within the preset range or the maximum deformation of the beam in the Z direction increases, the model is corrected and optimized again.

7. The method for designing a beam structure of a vertical machining center according to claim 1, characterized in that: In the step S1, the crossbeam and the column are connected by bolts, the saddle and the slider are connected by bolts, the upper guide rail and the crossbeam are connected by bolts, the side guide rail and the crossbeam are connected by bolts, the upper guide rail and the slider are clearance matched, and the side guide rail and the slider are clearance matched.

8. The method for designing a crossbeam structure of a vertical machining center according to claim 1, characterized in that: In the S2 step, the contact type between the crossbeam and the column is binding contact, the contact type between the saddle and the slider is binding contact, the contact type between the upper guide rail and the crossbeam is binding contact, the contact type between the side guide rail and the crossbeam is binding contact, the contact type between the upper guide rail and the slider is non-separation contact, and the contact type between the side guide rail and the slider is non-separation contact.

9. A beam structure designed according to the method for designing a beam structure of a vertical machining center according to any one of claims 1 to 8, characterized in that: It includes a motor, a saddle, a cross beam, an upper guide rail, a side guide rail, and two sliders. The upper guide rail is arranged on the upper end surface of the cross beam, and the side guide rail is arranged on the side end surface of the cross beam. The length directions of the upper guide rail and the side guide rail are parallel to the length direction of the cross beam. The mounting surface of the upper guide rail is perpendicular to the mounting surface of the side guide rail. The two sliders are arranged on the saddle and are slidably connected to the upper guide rail and the side guide rail respectively. The motor is arranged between the saddle and the cross beam, and the motor drives the saddle and the slider to move along the length direction of the cross beam.

10. The crossbeam structure of the vertical machining center according to claim 9, characterized in that: The cross-section of the saddle is L-shaped.

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