Moving-beam machine tool having internally constrained structure

Abstract

Disclosed in the present invention is a moving-beam machine tool having an internally constrained structure. The moving-beam machine tool comprises: a machine tool spindle, a rotary table and a bed, wherein at least two guide rails are provided in each of an X-axis direction, a Y-axis direction and a Z-axis direction, the at least two guide rails in the same axial direction include at least one pair of guide rails that are not on a same coordinate plane, and these guide rails form internal constraint spaces; the area where at least two internal constraint spaces overlap forms a motion space, and the motion space is a motion area of the tool tip of the machine tool spindle during machining; and the rotary table is fixedly arranged on the bed, and a workpiece on the rotary table is made to coincide with the motion space by means of the linear displacement of the machine tool spindle. By means of the provision of at least two guide rails that are not on the same coordinate plane in each of the three axial directions, the guide rail layout is optimized; and the guide rails are used to internally constrain the movement of machine tool components, so that the tool tip is always located in a closed space, and the movement of the tool tip in each axial direction is effectively constrained, thereby reducing the impact of a cutting force, and reducing micro-displacement. The impact of an overturning moment on the machine tool spindle is effectively avoided, thereby suppressing vibration and deformation, and ensuring the machining accuracy.

Description

A type of moving beam machine tool with internal constraint structure Technical Field

[0001] This invention relates to the field of machine tool technology, and in particular to a moving beam machine tool with an internal constraint structure. Background Technology

[0002] As the cornerstone of modern equipment manufacturing, CNC machine tools bear the strategic mission of providing key basic equipment for the manufacturing industry. Among them, moving-beam machine tools, with their movable beam and fixed worktable design, can reduce the influence of workpiece inertia, thereby improving the stability of the machining process, and are therefore highly favored by the high-end equipment manufacturing industry. Against the backdrop of the rapid development of high-end equipment manufacturing, the machine tool industry urgently needs to break through the performance bottlenecks of precision manufacturing technology. Especially in high-end manufacturing fields such as aerospace and precision instruments, with the exponential growth in the demand for ultra-precision machining, the requirements for the dynamic stability and machining accuracy of machine tools have approached physical limits. Research shows that when machining accuracy enters the sub-micron level, the sensitivity of the machine tool structure to force response will increase non-linearly. Especially during machine tool cutting, the dynamic cutting force borne by the tool system has significant time-varying characteristics and multi-degree-of-freedom coupling features. In carbide milling, the peak instantaneous cutting force generated in the tool-workpiece contact area can reach over 1,000 Newtons. This high-frequency alternating load triggers a three-dimensional dynamic response in the machine tool structure. The overturning moment induced by the cutting torque at the spindle-spindle mounting structure (beam, column, etc.) joint surface can cause micro-displacement of the tool cutting point, resulting in micron-level positional shifts in the tool system. This "butterfly effect" in precision machining not only directly affects the machining quality but also causes a systematic decay in machining accuracy through error propagation mechanisms.

[0003] Therefore, how to effectively control the impact of cutting force on the moving beam machine tool in order to improve the machining accuracy of the machine tool has become a technical problem that urgently needs to be solved. Summary of the Invention

[0004] This invention provides a moving beam machine tool with an internal constraint structure to effectively control the influence of cutting force on the moving beam machine tool.

[0005] To achieve the above objectives, the technical solution of the present invention is as follows:

[0006] A moving beam machine tool with an internally constrained structure includes: a machine tool spindle, a rotary table, and a bed, and further includes:

[0007] XY coordinate plane, YZ coordinate plane and ZX coordinate plane;

[0008] The XY coordinate plane is a plane perpendicular to the Z-axis direction;

[0009] The YZ coordinate plane is a plane perpendicular to the X-axis direction;

[0010] the ZX coordinate plane is a plane perpendicular to the Y-axis direction;

[0011] At least two guide rails are arranged in the X-axis direction, the Y-axis direction and the Z-axis direction, and at least one pair of guide rails in the same axis direction are not in the same coordinate plane;

[0012] The two XY coordinate planes and the two ZX coordinate planes in which the two X-direction guide rails in each pair of guide rails not in the same coordinate plane are located form an X-direction sub-space, and the union of the X-direction sub-spaces forms an X-direction inner constraint space;

[0013] The two XY coordinate planes and the two YZ coordinate planes in which the two Y-direction guide rails in each pair of guide rails not in the same coordinate plane are located form a Y-direction sub-space, and the union of the Y-direction sub-spaces forms a Y-direction inner constraint space;

[0014] The two ZX coordinate planes and the two YZ coordinate planes in which the two Z-direction guide rails in each pair of guide rails not in the same coordinate plane are located form a Z-direction sub-space, and the union of the Z-direction sub-spaces forms a Z-direction inner constraint space;

[0015] The overlapping region of at least two of the X-direction inner constraint space, the Y-direction inner constraint space and the Z-direction inner constraint space is a motion space, and the motion space is a motion region of a tool tip point of a main shaft of the machine tool in a machining process;

[0016] The rotary table is fixed on a bed, the main shaft of the machine tool is arranged on the bed through the X-direction guide rail, and the workpiece on the rotary table is coincided with the motion space through linear displacement of the main shaft of the machine tool.

[0017] Further, the motion space is a region in which the X-direction inner constraint space, the Y-direction inner constraint space and the Z-direction inner constraint space overlap.

[0018] Further, a motion plane is formed between the two guide rails not in the same coordinate plane in the same axis direction;

[0019] In a machining process, the tool tip point can coincide with the motion plane in the X-axis direction or the Y-axis direction.

[0020] Further, a motion plane is formed between the two guide rails not in the same coordinate plane in the same axis direction;

[0021] In at least one axis direction, the motion plane can pass through the workpiece on the rotary table.

[0022] Further, in the X-axis direction, the Y-axis direction and the Z-axis direction, at least one axis direction is provided with not less than three guide rails.

[0023] Furthermore, along the axial direction where there are no fewer than three guide rails, a prism-shaped space formed by using the guide rails as edges is the guide rail constraint space. The guide rail constraint space replaces the inner constraint space along the corresponding axial direction to form the motion space.

[0024] Furthermore, the bed includes a main body and a support column fixed on the main body, and two Y-guide rails not in the same coordinate plane are respectively set on the main body and the support column.

[0025] Furthermore, it also includes a crossbeam, which comprises a first body and a second body fixed to the first body;

[0026] The first main body is disposed on a Y-guide rail provided on the main body;

[0027] The second main body is mounted on the Y-guide rail provided on the support column;

[0028] Two X-guide rails, which are not in the same coordinate plane, are respectively set on the first body and the second body.

[0029] Furthermore, it also includes a slide saddle and a slide ram, wherein the slide ram is mounted on the slide saddle via a Z-guide rail, and the machine tool spindle is mounted on the slide ram;

[0030] The saddle is mounted on the X-guide rails provided on the crossbeam.

[0031] Furthermore, the sliding saddle includes a frame, a first extension, and a second extension;

[0032] The slide block is set inside the frame via a Z-guide rail;

[0033] The first extension extends from the frame along the Z-axis direction, and the first extension is disposed on the X-guide rail provided on the first main body.

[0034] The second extension extends from the frame along the X-axis direction and is disposed on the X-guide rail provided on the second main body.

[0035] Furthermore, the crossbeam also includes a side wall connecting the first body and the second body;

[0036] The first main body, the second main body, and the sidewalls form a space to accommodate the turntable and the support column.

[0037] Furthermore, it also includes a tilting milling head, in which two guide rails on the same axis but not on the same coordinate plane form a motion plane. During the machining process, the tilting axis of the tilting milling head intersects with at least one of the motion planes on the same axis, and the tip of the tilting milling head coincides with the intersection point.

[0038] Furthermore, the turntable is a dual-axis turntable, which can fix the workpiece, and the envelope of the part of the workpiece to be processed is within the motion space.

[0039] Furthermore, the swing angle milling head is a single swing angle milling head, and during the machining process, the swing axis of the swing angle milling head is located in the motion plane in at least one axial direction.

[0040] Furthermore, the tilting milling head is a double tilting milling head, and during the machining process, the tilting axis of the tilting milling head is located in the motion plane in at least one axial direction.

[0041] Furthermore, the tilting milling head is a non-orthogonal tilting milling head, and the tip of the non-orthogonal tilting milling head is located on the tilting axis of the non-orthogonal tilting milling head. Beneficial effects:

[0042] This invention provides a moving beam machine tool with an internal constraint structure. By setting at least one pair of guide rails not in the same coordinate plane in the X, Y, and Z directions, at least two of the X-direction, Y-direction, and Z-direction internal constraint spaces formed by the guide rails in the X, Y, and Z directions can intersect to form a closed motion space. This optimizes the guide rail structure layout and uses the guide rails to internally constrain the movement of the machine tool components, ensuring that the tool tip remains within the closed motion space during machining. This effectively constrains the tool tip in the X, Y, and Z directions, significantly reducing the impact of cutting forces on the tool tip and thus minimizing the micro-displacement of the tool tip. It also effectively avoids the overturning moment affecting the machine tool spindle during operation, suppresses vibration and deformation, and ensures the machining accuracy of the machine tool.

[0043] The machine tool spindle is mounted on the bed via guide rails. The linear displacement of the machine tool spindle ensures that the workpiece on the turntable fixed to the bed can coincide with the motion space. During the machining process, the workpiece does not need to undergo reciprocating linear displacement, reducing the influence of workpiece inertia and thus improving the stability of the machining process. Attached Figure Description

[0044] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0045] Figure 1 is a schematic diagram of a moving beam machine tool with an internal constraint structure disclosed in Embodiment 1 of the present invention;

[0046] Figure 2 is a structural schematic diagram of a moving beam machine tool with an internal constraint structure disclosed in Embodiment 1 of the present invention;

[0047] Figure 3 is a side view of a moving beam machine tool with an internal constraint structure disclosed in Embodiment 1 of the present invention;

[0048] Figure 4 is a front view of a moving beam machine tool with an internal constraint structure disclosed in Embodiment 1 of the present invention;

[0049] Figure 5 is a top view of a moving beam machine tool with an internal constraint structure disclosed in Embodiment 1 of the present invention;

[0050] Figure 6 is a schematic diagram of the bed structure of a moving beam machine tool with an internal constraint structure disclosed in Embodiment 1 of the present invention;

[0051] Figure 7 is a schematic diagram of the beam structure of a moving beam machine tool with an internal constraint structure disclosed in Embodiment 1 of the present invention;

[0052] Figure 8 is a schematic diagram of the slide saddle of a moving beam machine tool with an internal constraint structure disclosed in Embodiment 1 of the present invention;

[0053] Figure 9 is a schematic diagram of the X-direction internal constraint space of a moving beam machine tool with an internal constraint structure disclosed in Embodiment 1 of the present invention;

[0054] Figure 10 is a schematic diagram of the Y-direction internal constraint space of a moving beam machine tool with an internal constraint structure disclosed in Embodiment 1 of the present invention;

[0055] Figure 11 is a schematic diagram of the decomposition of Figure 10;

[0056] Figure 12 is a second exploded view of Figure 10;

[0057] Figure 13 is a schematic diagram of the Z-direction internal constraint space of a moving beam machine tool with an internal constraint structure disclosed in Embodiment 1 of the present invention;

[0058] Figure 14 is a schematic diagram of the guide rail constraint space in the Y-axis direction of a moving beam machine tool with an internal constraint structure disclosed in Embodiment 1 of the present invention.

[0059] Figure 15 is a schematic diagram of the guide rail constraint space in the Z-axis direction of a moving beam machine tool with an internal constraint structure disclosed in Embodiment 1 of the present invention.

[0060] Figure 16 is a schematic diagram of the cooperation between the tilting milling head and the slide of a moving beam machine tool with an internal constraint structure disclosed in Embodiment 2 of the present invention.

[0061] In the diagram: 1. Bed; 11. Main body; 12. Support column; 2. Swivel milling head; 3. Crossbeam; 31. First main body; 32. Second main body; 33. Side wall; 4. Saddle; 41. Frame; 42. First extension; 43. Second extension; 5. Roller; 6. Turntable; 71. First X-axis guide rail; 72. Second X-axis guide rail; 81. First Y-axis guide rail; 82. Second Y-axis guide rail; 83. Third Y-axis guide rail; 84. Fourth Y-axis guide rail; 91. First Z-axis guide rail; 92. Second Z-axis guide rail; 93. Third Z-axis guide rail; A1. Motion plane; X1. X-axis inward constraint space; Y1. Y-axis inward constraint space; Y11. First Y-axis subspace; Y12. Second Y-axis subspace; Y13. Third Y-axis subspace; Y14. Fourth Y-axis subspace; Z1, Z-direction inward constraint space; Z11, first Z-direction subspace; Z12, second Z-direction subspace; N, motion space. Detailed Implementation

[0062] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0063] Machine tool accuracy is affected by a variety of factors, including its structural design, drive and control systems, thermal errors, tool wear, and measurement and feedback systems. To improve machine tool accuracy, one can address these aspects or take comprehensive measures. Since the structural design of the machine tool is fundamental, optimizing its structure is the primary task for improving accuracy.

[0064] Currently, machine tools are mainly classified into horizontal machine tools, vertical machine tools, and gantry machine tools. The various components of these machine tools are connected in sequence to form an open chain structure, which inevitably leads to the formation of a cantilever structure for the machine tool spindle. However, the cutting force borne by the tool tip during machining is mainly applied to the connection between it and the adjacent components. This means that the rigidity of the machine tool will directly affect the stress state of the tool tip and the stability of machining accuracy.

[0065] Existing machine tool structures mainly improve the overall rigidity of the machine tool by enhancing the static rigidity of each component. However, in practical applications, it has been found that the dynamic rigidity of the machine tool components is insufficient under the influence of cutting force, gravity, and acceleration. This results in irregular micro-displacements at the tool tip, which significantly affects the machining accuracy of the machine tool. This makes us realize that improving the dynamic rigidity of the machine tool is particularly important for improving its machining accuracy.

[0066] Machine tools include linear motion axes and rotary axes to machine complex parts. This necessitates that the components of the linear axes be connected and supported by guide rails, which bear the forces and ensure motion accuracy. During machining, insufficient dynamic stiffness of the guide rails can lead to deformation, directly affecting the machining accuracy and reducing machining quality. This means that the dynamic stiffness of the machine tool largely depends on the dynamic stiffness of the guide rails. In other words, higher dynamic stiffness results in less impact on machining accuracy, while lower dynamic stiffness has a greater impact. However, due to limitations in material mechanics, improvements to guide rail dynamic stiffness are limited. Therefore, we need to address this issue from other angles to enhance guide rail dynamic stiffness.

[0067] Research and analysis revealed that current machine tool components typically employ dual guideways for linear motion support. Since these dual guideways are located in the same plane, they are susceptible to overturning moments during operation, leading to vibration and deformation, which is detrimental to the precision machining of the entire machine tool. Therefore, this application aims to improve the dynamic stiffness of the guideways by optimizing the machine tool's structural layout and guideway arrangement, thereby enhancing the overall rigidity of the machine tool.

[0068] Example 1:

[0069] This embodiment provides a moving crossbeam machine tool with an internally constrained structure, as shown in Figures 2 to 5, including: a machine tool spindle, a rotary table 6, and a bed 1, as shown in Figure 1, and further including:

[0070] XY coordinate plane, YZ coordinate plane and ZX coordinate plane;

[0071] The XY coordinate plane is a plane perpendicular to the Z-axis direction;

[0072] The YZ coordinate plane is a plane perpendicular to the X-axis direction;

[0073] The ZX coordinate plane is a plane perpendicular to the Y-axis direction;

[0074] At least two guide rails are provided in the X-axis, Y-axis and Z-axis directions, and at least one pair of guide rails that are not in the same coordinate plane exist in the same direction.

[0075] Each pair of X-guides that are not in the same coordinate plane contains two XY coordinate planes and two ZX coordinate planes, which form an X-direction subspace. The union of the X-direction subspaces forms the X-direction inner constraint space X1.

[0076] Each pair of Y-guides that are not in the same coordinate plane contains two XY coordinate planes and two YZ coordinate planes, which form a Y-direction partition space. The union of the Y-direction partition spaces forms the Y-direction inner constraint space Y1.

[0077] Each pair of Z-guides that are not in the same coordinate plane contains two ZX coordinate planes and two YZ coordinate planes, which form a Z-direction subspace. The union of the Z-direction subspaces forms the Z-direction inner constraint space Z1.

[0078] The region in which at least two of the X-direction inward constraint space X1, Y-direction inward constraint space Y1, and Z-direction inward constraint space Z1 overlap is the motion space N. The motion space N is the motion region of the tool tip of the machine tool spindle during the machining process. The tool tip is the point that the tool tip of the machine tool spindle needs to reach.

[0079] The rotary table 6 is fixed on the bed 1, and the machine tool spindle is set on the bed 1 via the X-axis guide rail. Through the linear displacement of the machine tool spindle, the workpiece on the rotary table 6 coincides with the motion space N.

[0080] This embodiment provides a moving beam machine tool with an internal constraint structure. By setting at least one pair of guide rails (two guide rails forming a pair) in the X, Y, and Z axes respectively, which are not in the same coordinate plane, at least two of the X-axis internal constraint spaces X1, Y-axis internal constraint spaces Y1, and Z-axis internal constraint spaces formed by the guide rails in the X, Y, and Z axes can intersect to form a closed motion space N. This optimizes the guide rail structure layout and uses the guide rails to internally constrain the movement of the machine tool components, ensuring that the tool tip is always located within the closed motion space N during machining. This achieves effective constraint on the tool tip in the X, Y, and Z axes, significantly reducing the impact of cutting forces on the tool tip and thus reducing the micro-displacement of the tool tip. It effectively avoids the overturning moment affecting the machine tool spindle during operation, suppresses vibration and deformation, and ensures the machining accuracy of the machine tool.

[0081] The machine tool spindle is mounted on the bed 1 via guide rails. Through the linear displacement of the machine tool spindle, the workpiece fixed on the rotary table 6 of the bed 1 can be aligned with the motion space N. During the machining process, the workpiece does not need to undergo reciprocating linear displacement, reducing the influence of workpiece inertia and thus improving the stability of the machining process.

[0082] In this embodiment, to facilitate the construction of various spaces and planes, the guide rail needs to be conceptualized as a line within the space, serving as a reference for the construction of the space and plane;

[0083] Specifically, when the area of ​​the guide rail used to support machine tool components is the guide rail surface of the guide rail itself (taking Figure 4 as an example, the first X guide rail 71 in Figure 4 meets this working condition), the guide rail can be conceptualized as the center line of the guide rail surface;

[0084] When the area of ​​the guide rail used to support machine tool components is the edge line on both sides of the guide rail surface itself (taking Figure 4 as an example, the second X guide rail 72 in Figure 4 meets this working condition), the guide rail can be conceptualized as the edge line of the guide rail surface.

[0085] In this embodiment, the coordinate planes include the XY coordinate plane, the YZ coordinate plane, and the ZX coordinate plane;

[0086] The XY coordinate plane is a plane parallel to the XY plane, mathematically called the z=k plane, whose normal vector is the same as that of the standard XY plane, where k is a constant;

[0087] The YZ coordinate plane is a plane parallel to the YZ plane, mathematically called the x=k plane, whose normal vector is the same as that of the standard YZ plane, where k is a constant;

[0088] The ZX coordinate plane is a plane parallel to the ZX plane, mathematically called the y=k plane, whose normal vector is the same as that of the standard ZX plane, where k is a constant.

[0089] For the guide rails in the X-axis direction, the constant k corresponding to the two XY coordinate planes (z=k plane) where the two X guide rails are not in the same coordinate plane are not equal.

[0090] For each pair of X-guides that are not in the same coordinate plane, the two ZX coordinate planes (y=k plane) where they are located have different constants k.

[0091] The X-axis partition space is a quadrangular prism space with open ends, enclosed by two XY coordinate planes and two ZX coordinate planes where each pair of X-axis guides that are not in the same coordinate plane are located.

[0092] When the number of X-guides is equal to 2, there is only one pair of X-guides that are not in the same coordinate plane. Therefore, there is only one X-direction partition space. At this time, the X-direction inner constraint space X1 is equal to the X-direction partition space.

[0093] When the number of X-axis guides is greater than 2, each additional pair of X-axis guides that are not in the same coordinate plane will add an X-axis subspace. At this time, the X-axis inner constraint space X1 is equal to the union of multiple X-axis subspaces.

[0094] For guide rails in the Y-axis direction, the constant k corresponding to the two XY coordinate planes (z=k plane) where each pair of Y guide rails is not in the same coordinate plane is not equal.

[0095] For each pair of Y-guides that are not in the same coordinate plane, the two YZ coordinate planes (x = k plane) where they are located have different constants k.

[0096] The Y-axis partition space is a quadrangular prism space with open ends, enclosed by two XY coordinate planes and two YZ coordinate planes where each pair of Y-guides that are not in the same coordinate plane are located.

[0097] When the number of Y-guides is equal to 2, there is only one pair of Y-guides that are not in the same coordinate plane. Therefore, there is only one Y-direction partition space. At this time, the Y-direction inner constraint space Y1 is equal to the Y-direction partition space.

[0098] When the number of Y-guides is greater than 2, each additional pair of Y-guides that are not in the same coordinate plane will add a corresponding Y-axis subspace. At this time, the Y-axis inner constraint space Y1 is equal to the union of multiple Y-axis subspaces.

[0099] For guide rails in the Z-axis direction, the constant k corresponding to the two ZX coordinate planes (y=k plane) where each pair of Z guide rails is not in the same coordinate plane is not equal.

[0100] For each pair of Z-guides that are not in the same coordinate plane, the two ZY coordinate planes (x = k plane) have different constants k.

[0101] The Z-axis partition space is a quadrangular prism space with open ends, enclosed by two ZX coordinate planes and two YZ coordinate planes where each pair of Z-guides that are not in the same coordinate plane are located.

[0102] When the number of Z-guides is equal to 2, there is only one pair of Z-guides that are not in the same coordinate plane. Therefore, there is only one Z-axis partition space. At this time, the Z-axis inner constraint space Z1 is equal to the Z-axis partition space.

[0103] When the number of Z-guides is greater than 2, each additional pair of Z-guides that are not in the same coordinate plane will add a corresponding Z-axis subspace. At this time, the Z-axis inner constraint space Z1 is equal to the union of multiple Z-axis subspaces.

[0104] In a specific embodiment, as shown in Figure 1, the motion space N is the overlapping region of the X-direction inward constraint space X1, the Y-direction inward constraint space Y1, and the Z-direction inward constraint space Z1.

[0105] By merging the X-axis inward constraint space X1, the Y-axis inward constraint space Y1, and the Z-axis inward constraint space Z1 to form a closed motion space, the tool tip can remain within this closed space throughout its movement in the three directions during machining. During machining, the cutting force on the tool tip is confined within this motion space. A pair of guide rails, not lying on the same coordinate plane, consistently support the tool tip from both ends, optimizing the force on the guide rails. Simultaneously, the machine tool components moving in the three axes also maintain support at both ends, optimizing the force on the guide rails and providing support and limitation for the machine tool components. Ultimately, this structural layout eliminates weak points and areas with insufficient dynamic stiffness, thereby improving the overall rigidity of the machine tool, reducing the micro-displacement of the tool tip, avoiding the influence of overturning moments, suppressing vibration and deformation, and ensuring the machining stability of the tool tip.

[0106] At the same time, the improvement of dynamic stiffness can also reduce the wear and aging of machine tools, ensure the machining accuracy of machine tools, and extend the service life of machine tools.

[0107] Furthermore, since the motion space N is formed by the guide rails, the motion space N must be between a pair of guide rails that are not in the same coordinate plane in the three axes. This means that the motion area must be located inside the machine tool's support structure. Compared with the existing machine tool's support structure (bed, column, saddle, and ram, etc.), which can only provide support outside the motion area of ​​the tool tip, the machine tool of this application can reduce its volume and weight when achieving the same size machining area, thereby improving the overall rigidity of the machine tool and reducing its cost.

[0108] In a specific embodiment, as shown in Figure 4, a motion plane A1 is formed between two guide rails on the same axis but not in the same coordinate plane;

[0109] During the machining process, the tool tip can coincide with the motion plane A1 in the X-axis or Y-axis direction.

[0110] When the tool tip coincides with the motion plane A1, the motion plane A1 supports the tool tip, and the tool tip will not form a cantilever structure relative to the motion plane A1, thus ensuring that the tool tip maintains stable accuracy during the machining of the plane.

[0111] The motion plane A1 is established by adopting the aforementioned method of conceptualizing the guide rail as a line in space. The line formed by two guide rails conceptualized on the same axis but not in the same coordinate plane, the plane in which they are located is the motion plane A1.

[0112] In a specific embodiment, as shown in Figure 4, a motion plane A1 is formed between two guide rails on the same axis but not in the same coordinate plane;

[0113] In at least one axial direction, the motion plane A1 can pass through the workpiece on the turntable 6.

[0114] The moving plane A1 supports the workpiece, reducing the impact of cutting force on the workpiece position, thereby maintaining stable accuracy during machining.

[0115] In a specific embodiment, at least three guide rails are provided in at least one of the X-axis, Y-axis and Z-axis directions.

[0116] At least three guide rails are used for over-positioning. Adding extra positioning constraints restricts the guide rails' degrees of freedom in multiple directions, allowing them to withstand greater lateral and torsional forces, thus improving their dynamic stiffness and reducing positioning errors caused by guide rail loosening or deformation. Furthermore, it increases the support points for the connected machine tool components, improving the dynamic stiffness of those components. Simultaneously, it ensures consistency in each positioning, improves repeatability, and meets the demands of high-precision machining.

[0117] In a specific embodiment, along the axial direction provided with no less than three guide rails, a prism-shaped space formed by the guide rails as edges is used as the guide rail constraint space. The guide rail constraint space replaces the inner constraint space along the corresponding axial direction to form the motion space. A constraint surface is formed between two adjacent guide rails, and multiple constraint surfaces are connected to form the guide rail constraint space along the corresponding axial direction.

[0118] The constraint surface is established by adopting the aforementioned method of conceptualizing the guide rail as a line in space. On the axis with no less than three guide rails, the plane formed by the conceptualization of two adjacent guide rails is the constraint surface.

[0119] The constraint surfaces are connected to form a guide rail constraint space along the corresponding axis, which is a prism-shaped space formed by lines formed by conceptualization as edges;

[0120] Along the same axis, the guide rail constraint space is located within the inner constraint space. Although both are based on the lines formed by the conceptualization of the guide rail as the reference for establishing the space, compared to the quadrangular prism inner constraint space formed by coordinate surfaces, the guide rail constraint space along the corresponding axis, formed by the connection of constraint surfaces, allows the tool tip to be completely within the bounded area of ​​the guide rail. The tool tip will not form a cantilever structure relative to the guide rail in this direction, resulting in a better constraint effect. This further improves the dynamic stiffness of the tool tip, reduces the influence of cutting force on the tool tip, and reduces the micro-displacement of the tool tip.

[0121] In a specific embodiment, the machine tool spindle is mounted on the bed 1 via X-axis guide rails, Y-axis guide rails and Z-axis guide rails, enabling the machine tool spindle to perform linear displacement along the X-axis, Y-axis and Z-axis directions.

[0122] In a specific embodiment, as shown in FIG6, the bed 1 includes a main body 11 and a support column 12 fixed on the main body 11, and two Y-guide rails not in the same coordinate plane are respectively arranged on the main body 11 and the support column 12.

[0123] In this embodiment, both the main body 11 and the support column 12 are provided with two Y-guide rails;

[0124] Specifically, the main body 11 is provided with a third Y-guide rail 83 and a fourth Y-guide rail 84, and the support column 12 is provided with a first Y-guide rail 81 and a second Y-guide rail 82.

[0125] Four Y-guide rails (first Y-guide rail 81, second Y-guide rail 82, third Y-guide rail 83 and fourth Y-guide rail 84) form four pairs of Y-guide rails that are not in the same coordinate plane, as shown in Figures 10 and 12, which constitute four Y-direction subspaces (first Y-guide rail 81 and third Y-guide rail 83 constitute the first Y-direction subspace Y11, second Y-guide rail 82 and fourth Y-guide rail 84 constitute the second Y-direction subspace Y12, second Y-guide rail 82 and third Y-guide rail 83 constitute the third Y-direction subspace Y13, first Y-guide rail 81 and fourth Y-guide rail 84 constitute the fourth Y-direction subspace Y14). The union of the four Y-direction subspaces is the Y-direction inner constraint space Y1.

[0126] As shown in Figure 14, the space enclosed by the four constraint surfaces formed by the four Y-axis guide rails is the guide rail constraint space in the Y-axis direction.

[0127] By setting part of the Y-guide rail on the support column 12, a stable and reliable support is provided for the Y-guide rail, which suppresses vibration and deformation and helps to ensure the dynamic stiffness of the Y-guide rail.

[0128] In a specific embodiment, as shown in Figures 2 to 5, a crossbeam 3 is also included. As shown in Figure 7, the crossbeam 3 includes a first body 31 and a second body 32 fixed on the first body 31.

[0129] The first main body 31 is disposed on the third Y guide rail 83 and the fourth Y guide rail 84 provided on the main body 11;

[0130] The second main body 32 is disposed on the first Y-guide rail 81 and the second Y-guide rail 82 provided on the support column 12;

[0131] Two X-guide rails that are not in the same coordinate plane are respectively set on the first body 31 and the second body 32;

[0132] In this embodiment, the crossbeam 3 is provided with two X-guide rails (first X-guide rail 71 and second X-guide rail 72), the first main body 31 is provided with the second X-guide rail 72, and the second main body 32 is provided with the first X-guide rail 71. The first X-guide rail 71 and the second X-guide rail 72 constitute an X-direction subspace, as shown in Figure 9. The X-direction subspace is equivalent to the X-direction inner constraint space X1.

[0133] In a specific embodiment, as shown in Figures 2 to 5, it also includes a slide saddle 4 and a slide ram 5. The slide ram 5 is mounted on the slide saddle 4 via a Z-guide rail, and the machine tool spindle is mounted on the slide ram 5.

[0134] The sliding saddle 4 is mounted on the X-guide rail provided on the crossbeam 3;

[0135] In this embodiment, as shown in FIG8, the sliding saddle 4 includes a frame 41, a first extension 42 and a second extension 43;

[0136] The slide ram 5 is installed inside the frame 41 via three Z-guide rails (first Z-guide rail 91, second Z-guide rail 92 and third Z-guide rail 93);

[0137] The first extension 42 extends from the frame 41 along the Z-axis direction, and the first extension 42 is disposed on the second X-guide rail 72 provided on the first main body 31.

[0138] The second extension 43 extends from the frame 41 along the X-axis direction, and the second extension 43 is disposed on the first X-guide rail 71 provided on the second main body 32;

[0139] By providing a first extension 42 and a second extension 43, the slide saddle 4 ensures that there is enough space at the bottom of the frame 41 to facilitate the layout of other machine tool components.

[0140] The first Z-guide rail 91, the second Z-guide rail 92, and the third Z-guide rail 93 form two pairs of Z-guide rails that are not in the same coordinate plane, as shown in Figure 13. They constitute two Z-direction subspaces (the first Z-direction subspace Z11 and the second Z-direction subspace Z12). The union of the two Z-direction subspaces is the Z-direction inner constraint space Z1.

[0141] As shown in Figure 15, the space enclosed by the three constraint surfaces formed by the three Z-axis guide rails 9 is the guide rail constraint space in the Z-axis direction.

[0142] In a specific embodiment, as shown in FIG7, the crossbeam 3 further includes a side wall 33 connecting the first body 31 and the second body 32;

[0143] The first main body 31, the second main body 32 and the side wall 33 form a space to accommodate the turntable 6 and the support column 12. This layout can not only make full use of the high static stiffness of the side wall 33 to provide stable support for the X guide rail, but also improve space utilization and reduce the overall space occupied by the machine tool.

[0144] Example 2:

[0145] This embodiment provides a moving beam machine tool with an internally constrained structure. The main structure of this embodiment is the same as that of Embodiment 1. The difference between this embodiment and Embodiment 1 is as follows:

[0146] In this embodiment, a swing milling head 2 is also included. A motion plane A1 is formed between two guide rails on the same axis but not on the same coordinate plane, as shown in Figure 16. The swing milling head 2 is set on the slide ram 5. During the machining process, the swing axis of the swing milling head 2 intersects with at least one of the motion planes A1 on the same axis, and the tip of the swing milling head coincides with the intersection point.

[0147] In this embodiment, the tip of the tilting milling head 2 is the same concept as the tip of the machine tool spindle in Embodiment 1.

[0148] When the tip of the oscillating milling head 2 coincides with the motion plane A1, the motion plane A1 supports the tip, and the tip does not form a cantilever structure relative to the motion plane A1. This reduces the impact of cutting force on the displacement of the tip relative to the oscillating axis, thereby ensuring the stability of the tip's accuracy during machining.

[0149] Preferably, the swing angle milling head 2 can be a single swing angle milling head, and during the machining process, the swing axis of the swing angle milling head 2 is located in at least one axial motion plane A1.

[0150] Preferably, the oscillating milling head 2 can be a double oscillating milling head, and during the machining process, the oscillation axis of the oscillating milling head 2 is located within the motion plane A1 in at least one axial direction.

[0151] Preferably, the oscillating milling head 2 can be a non-orthogonal oscillating milling head, and the tip of the non-orthogonal oscillating milling head is located on the oscillation axis of the non-orthogonal oscillating milling head.

[0152] Example 3:

[0153] This embodiment provides a moving beam machine tool with an internally constrained structure. The main structure of this embodiment is the same as that of Embodiment 1. The difference between this embodiment and Embodiment 1 is as follows:

[0154] In this embodiment, the turntable 6 is a dual-axis turntable. The turntable 6 can fix the workpiece, and the envelope of the part of the workpiece to be processed is within the motion space, ensuring that the part of the workpiece to be processed can be within the motion space during the processing. The turntable 6 can be a cradle turntable or a vertical / horizontal 90° indexing worktable, or other forms of dual-axis turntable.

[0155] The envelope of a workpiece is composed of a series of feature lines, which are the trajectories of the points where the cutting tool is tangent to the workpiece surface during machining. As the cutting tool moves along a certain trajectory, these feature lines continuously change and eventually form the envelope of the workpiece.

[0156] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present invention.

Claims

1. A moving beam machine tool with an internally constrained structure, comprising: The machine tool spindle, rotary table (6), and bed (1) are characterized in that they further include: XY coordinate plane, YZ coordinate plane and ZX coordinate plane; The XY coordinate plane is a plane perpendicular to the Z-axis direction; The YZ coordinate plane is a plane perpendicular to the X-axis direction; The ZX coordinate plane is a plane perpendicular to the Y-axis direction; At least two guide rails are provided in the X-axis, Y-axis and Z-axis directions, and at least one pair of guide rails that are not in the same coordinate plane exist in the same axis. Each pair of X-guides that are not in the same coordinate plane contains two XY coordinate planes and two ZX coordinate planes, which form an X-direction partition space. The union of the X-direction partition spaces forms an X-direction inner constraint space. Each pair of Y-guides that are not in the same coordinate plane contains two XY coordinate planes and two YZ coordinate planes, which form a Y-direction partition space. The union of the Y-direction partition spaces forms the Y-direction inner constraint space. Each pair of Z-guides that are not in the same coordinate plane contains two ZX coordinate planes and two YZ coordinate planes, which form a Z-direction partition space. The union of the Z-direction partition spaces forms a Z-direction inner constraint space. The region in which at least two of the X-direction inward constraint space, Y-direction inward constraint space and Z-direction inward constraint space overlap is the motion space, which is the motion area of ​​the tool tip of the machine tool spindle during the machining process; The rotary table (6) is fixed on the bed (1), and the machine tool spindle is set on the bed (1) through the X-guide rail. Through the linear displacement of the machine tool spindle, the workpiece on the rotary table (6) coincides with the motion space. The bed (1) includes a main body (11) and a support column (12) fixed on the main body (11). Two Y-guide rails that are not in the same coordinate plane are respectively set on the main body (11) and the support column (12). It also includes a crossbeam (3), which includes a first body (31) and a second body (32) fixed on the first body (31); The first body (31) is disposed on the Y-guide rail provided on the body (11); The second main body (32) is mounted on the Y-guide rail provided on the support column (12); Two X-guide rails that are not in the same coordinate plane are respectively set on the first body (31) and the second body (32); It also includes a slide saddle (4) and a slide ram (5), wherein the slide ram (5) is mounted on the slide saddle (4) via a Z-guide rail, and the machine tool spindle is mounted on the slide ram (5); The slide saddle (4) is mounted on the X-guide rail provided on the crossbeam (3); The sliding saddle (4) includes a frame (41), a first extension (42), and a second extension (43); The slide (5) is set inside the frame (41) via a Z-guide rail; The first extension (42) extends from the frame (41) along the Z-axis direction, and the first extension (42) is disposed on the X-guide rail provided on the first main body (31); The second extension (43) extends from the frame (41) along the X-axis direction, and the second extension (43) is disposed on the X-guide rail provided on the second main body (32); The crossbeam (3) also includes a side wall (33) connecting the first body (31) and the second body (32); The first body (31), the second body (32), and the side wall (33) form a space to accommodate the turntable (6) and the support column (12).

2. The moving beam machine tool with an internal constraint structure according to claim 1, characterized in that, The motion space is the region where the X-direction inward constraint space, the Y-direction inward constraint space, and the Z-direction inward constraint space overlap.

3. The moving beam machine tool with an internal constraint structure according to claim 1, characterized in that, A motion plane is formed between two guide rails on the same axis but not in the same coordinate plane; During the machining process, the tool tip can coincide with the motion plane in the X-axis or Y-axis direction.

4. A moving beam machine tool with an internal constraint structure according to claim 1, characterized in that, A motion plane is formed between two guide rails on the same axis but not in the same coordinate plane; In at least one axial direction, the motion plane can pass through the workpiece on the turntable (6).

5. A moving beam machine tool with an internal constraint structure according to claim 1, characterized in that, In the X-axis, Y-axis and Z-axis directions, at least three guide rails are provided in at least one axis.

6. A moving beam machine tool with an internal constraint structure according to claim 5, characterized in that, Along an axial direction with no fewer than three guide rails, a prism-shaped space formed by the guide rails as edges is called the guide rail constraint space. The guide rail constraint space replaces the inner constraint space along the corresponding axial direction to form the motion space.

7. A moving beam machine tool with an internal constraint structure according to claim 1, characterized in that, It also includes a swing milling head (2), in which two guide rails on the same axis but not on the same coordinate plane form a motion plane. During the machining process, the swing axis of the swing milling head (2) intersects with the motion plane on at least one axis, and the tip of the swing milling head (2) coincides with the intersection point.

8. A moving beam machine tool with an internal constraint structure according to claim 1, characterized in that, The turntable (6) is a dual-axis turntable, which can fix the workpiece, and the envelope of the part of the workpiece to be processed is within the motion space.

9. A moving beam machine tool with an internal constraint structure according to claim 7, characterized in that, The swing angle milling head (2) is a single swing angle milling head. During the machining process, the swing axis of the swing angle milling head is located in the motion plane in at least one axial direction.

10. A moving crossbeam machine tool with an internal constraint structure according to claim 7, characterized in that, The swing angle milling head (2) is a double swing angle milling head. During the machining process, the swing axis of the swing angle milling head is located in the motion plane in at least one axial direction.

11. A moving beam machine tool with an internal constraint structure according to claim 7, characterized in that, The swing angle milling head (2) is a non-orthogonal swing angle milling head, and the tip of the non-orthogonal swing angle milling head is located on the swing axis of the non-orthogonal swing angle milling head.

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