Dynamic vibration damping device and cutting tool system

Abstract

This application belongs to the field of cutting tool technology, specifically relating to a dynamic vibration damping device and a cutting tool system. The dynamic vibration damping device includes: a base assembly; a mass unit spaced apart from the base assembly along the axial direction of the vibration axis; a damping assembly including multiple beam members spaced apart circumferentially along the vibration axis, the multiple beam members passing through the base assembly and the mass unit; and a damping unit disposed on the side of the mass unit away from the base assembly. The damping unit includes a retaining ring and multiple damping elements, the multiple damping elements being disposed between the retaining ring and the mass unit. At least one damping element forms a first connection with the axis of the vibration axis, and at least another damping element forms a second connection with the axis of the vibration axis. The orthographic projections of the first and second connections in a plane perpendicular to the axis of the vibration axis are perpendicular to each other. This application can effectively suppress chatter caused by the structural characteristics of structures with large aspect ratios during machining, improving the machining accuracy and stability of the workpiece.

Description

Technical Field

[0001] This application relates to the field of cutting tool technology, and more specifically, to a dynamic vibration damping device and a cutting tool system. Background Technology

[0002] Cutting chatter is one of the biggest obstacles to improving the machining accuracy and lifespan of cutting tools. Therefore, seeking effective and reliable technologies to suppress harmful vibrations is of great practical significance. Among the many existing vibration suppression technologies, dynamic vibration absorption devices absorb and dissipate the vibration of the main structure in the form of a secondary vibration subsystem. Compared with other vibration suppression methods (such as vibration isolation and energy dissipation vibration reduction), they have advantages such as simple structure and high feasibility, and are therefore widely used in practical engineering problems.

[0003] In machining processes, especially for parts with deep holes or cavities, the machining system often features a large length-to-diameter ratio (L / D ratio). However, this large L / D ratio results in weak end-effector stiffness, making the tool and workpiece prone to harmful relative motion during milling, leading to severe chatter. Chatter not only reduces part accuracy and surface quality and shortens tool life but also increases machining costs, severely impacting machining efficiency and quality. Summary of the Invention

[0004] The purpose of this application is to provide a dynamic vibration damping device and a tool system, which can effectively suppress the chatter caused by the structural characteristics of the large aspect ratio structure in the process system during the machining process, thereby improving the machining accuracy and stability of the workpiece.

[0005] In a first aspect, embodiments of this application provide a dynamic vibration damping device for being sleeved on the end of a vibration shaft. The dynamic vibration damping device includes: a base assembly; a mass unit spaced apart from the base assembly along the axial direction of the vibration shaft; a stiffness assembly including a plurality of beam members spaced apart circumferentially along the vibration shaft, the plurality of beam members passing through the base assembly and the mass unit; and a damping unit disposed on the side of the mass unit away from the base assembly. The damping unit includes a retaining ring and a plurality of damping elements, the plurality of damping elements being disposed between the retaining ring and the mass unit. At least one damping element forms a first connection with the axis of the vibration shaft, and at least another damping element forms a second connection with the axis of the vibration shaft. The orthographic projections of the first connection and the second connection in a plane perpendicular to the axis of the vibration shaft are perpendicular to each other.

[0006] In addition, the dynamic vibration absorption device according to this application may also have the following additional technical features:

[0007] In some embodiments of this application, the retaining ring includes a first clamp and a second clamp that are disposed around the outer periphery of the vibration shaft and connected to each other. The first clamp is provided with a first protrusion extending outward along its own radial direction, and the second clamp is provided with a second protrusion extending outward along its own radial direction. The first protrusion and the second protrusion are respectively fixedly connected to corresponding damping elements.

[0008] In some embodiments of this application, the first protrusion and the second protrusion are respectively provided with grooves on the side facing the mass unit. The length direction of the grooves is parallel to the axis of the vibration shaft, and the damping element is embedded in the groove and contacts the mass unit.

[0009] In some embodiments of this application, the first clamp is provided with a first positioning ear at both ends along its circumference, and the second clamp is provided with a second positioning ear at both ends along its circumference. The first positioning ear and the second positioning ear are connected by a first fastener.

[0010] In some embodiments of this application, the base assembly includes a first clamping hoop and a second clamping hoop that are disposed around the outer periphery of the vibration shaft and connected to each other. The first clamping hoop is provided with a first mounting portion extending outward along its own radial direction, and the second clamping hoop is provided with a second mounting portion extending outward along its own radial direction. The first mounting portion and the second mounting portion are respectively fixedly connected to one end of the beam member by fastening components.

[0011] In some embodiments of this application, the first clamping hoop is provided with third positioning ears at both ends along its circumference, and the second clamping hoop is provided with fourth positioning ears at both ends along its circumference. The third positioning ears and the fourth positioning ears are connected by a second fastener.

[0012] In some embodiments of this application, the mass unit is provided with a plurality of third mounting parts at intervals along its circumference, and the third mounting parts are fixedly connected to one end of the beam member by fastening components.

[0013] In some embodiments of this application, the number of damping elements is four, and the four damping elements are arranged in a centrally symmetrical manner with respect to the axis of the vibration shaft; and / or, the number of beam members is four, and the four beam members are arranged in a centrally symmetrical manner with respect to the axis of the vibration shaft.

[0014] In some embodiments of this application, the mass unit is made of steel, the base assembly, stiffness assembly and retaining ring are all made of aluminum alloy, and the damping component is made of rubber or granular stone.

[0015] Secondly, embodiments of this application provide a cutting tool system, including: a cutting tool, including a tool holder and a cutting head, wherein the axis of the cutting head and the axis of the tool holder are set at a preset angle; and a dynamic vibration damping device according to embodiments of this application, wherein the dynamic vibration damping device is sleeved on the outer periphery of the tool holder.

[0016] According to the embodiments of this application, the dynamic vibration absorption device and the tool system are sleeved on the outer periphery of the tool holder. The vibration energy of the tool holder is transferred to the mass unit through the damping unit. At least two damping elements of the damping unit have mutually orthogonal translational degrees of freedom to suppress the vibration of the tool in two mutually orthogonal directions. This effectively suppresses the chatter caused by the large length-to-diameter ratio structural features in the process system during the machining process due to their own structural characteristics, thereby improving the machining accuracy and cutting stability of the workpiece.

[0017] The above description is only an overview of the technical solution of this application. In order to better understand the technical means of this application and to implement it in accordance with the contents of the specification, and to make the above and other objects, features and advantages of this application more obvious and understandable, the following are specific embodiments of this application. Attached Figure Description

[0018] Various other advantages and benefits will become apparent to those skilled in the art upon reading the following detailed description of preferred embodiments. The accompanying drawings are for illustrative purposes only and are not intended to limit the scope of this application. Furthermore, the same reference numerals denote the same parts throughout the drawings. Wherein:

[0019] Various other advantages and benefits will become apparent to those skilled in the art upon reading the following detailed description of preferred embodiments. The accompanying drawings are for illustrative purposes only and are not intended to limit the scope of this application. Furthermore, the same reference numerals denote the same parts throughout the drawings. Wherein:

[0020] Figure 1 This is a schematic diagram of the tool system according to an embodiment of this application;

[0021] Figure 2 for Figure 1 The diagram shows the simulation results of the modal vibration modes of the cutting tool.

[0022] Figure 3 This is a schematic diagram of the structure of the dynamic vibration absorption device according to an embodiment of this application;

[0023] Figure 4 for Figure 3 The diagram shown is an exploded view of the dynamic vibration absorption device.

[0024] Figure 5 This is a schematic diagram of the simulation results of the main vibration mode shape of the dynamic vibration absorption device according to an embodiment of this application;

[0025] Figure 6 for Figure 2 A schematic diagram showing the frequency response function measurement results at the first measuring point of the cutting tool;

[0026] Figure 7 for Figure 2 The diagram shows the frequency response function measurement results at the second measuring point of the cutting tool.

[0027] Figure 8 To adopt Figure 1 The image shows a comparison of the surface quality of the workpiece cut by the tool system and the tool without the added power vibration damping device.

[0028] The labels in the attached diagram are as follows:

[0029] 100. Dynamic vibration damping device;

[0030] 1. Base assembly; 11. First clamping clamp; 12. Second clamping clamp; 13. First mounting part; 14. Second mounting part; 15. Fastening assembly; 16. Third positioning ear; 17. Fourth positioning ear; 18. Second fastener;

[0031] 2. Mass unit; 21. Third installation section;

[0032] 3. Stiffness components; 31. Beam members;

[0033] 4. Damping unit; 41. Snap ring; 411. First clamp; 412. Second clamp; 413. First protrusion; 414. Second protrusion; 415. First positioning ear; 416. Second positioning ear; 42. Damping component; 43. First fastener;

[0034] 200. Cutting tool; 210. Tool holder; 220. Tool tip; a. First measuring point; b. Second measuring point. Detailed Implementation

[0035] Exemplary embodiments of this application will now be described in more detail with reference to the accompanying drawings. While exemplary embodiments of this application are shown in the drawings, it should be understood that this application may be implemented in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided to enable a more thorough understanding of this application and to fully convey the scope of this application to those skilled in the art.

[0036] It should be understood that the terminology used herein is for the purpose of describing particular exemplary embodiments only and is not intended to be limiting. Unless the context clearly indicates otherwise, the singular forms “a,” “an,” and “described” as used herein may also include the plural forms. The terms “comprising,” “including,” “containing,” and “having” are inclusive and therefore indicate the presence of the stated features, steps, operations, elements, and / or components, but do not exclude the presence or addition of one or more other features, steps, operations, elements, components, and / or combinations thereof. The method steps, processes, and operations described herein are not construed as requiring them to be performed in a particular order described or illustrated unless the order of performance is explicitly indicated. It should also be understood that additional or alternative steps may be used.

[0037] Although terms such as first, second, third, etc., may be used in this document to describe multiple elements, components, regions, layers, and / or segments, these elements, components, regions, layers, and / or segments should not be limited by these terms. These terms may be used only to distinguish one element, component, region, layer, or segment from another. Unless the context clearly indicates otherwise, terms such as "first," "second," and other numerical terms used herein do not imply order or sequence. Therefore, the first element, component, region, layer, or segment discussed below may be referred to as the second element, component, region, layer, or segment without departing from the teachings of the exemplary embodiments.

[0038] For ease of description, spatial relative terms may be used in the text to describe the relationship of one element or feature relative to another element or feature, as shown in the figure. These relative terms include, for example, "inside," "outside," "middle," "outer," "below," "below," "above," "over," etc. Such spatial relative terms are intended to include different orientations of the device in use or operation, other than those depicted in the figure. For example, if the device in the figure is flipped, an element described as "below other elements or features" or "below other elements or features" would subsequently be oriented as "above other elements or features" or "above other elements or features." Therefore, the example term "below" can include both upper and lower orientations. The device may be otherwise oriented (rotated 90 degrees or in other directions), and the spatial relative descriptors used in the text will be interpreted accordingly.

[0039] In this document, the term "embodiment" means that a particular feature, structure, or characteristic described in connection with an embodiment may be included in at least one embodiment of this application. The appearance of this phrase in various places throughout the specification does not necessarily refer to the same embodiment, nor is it a separate or alternative embodiment mutually exclusive with other embodiments. It will be explicitly and implicitly understood by those skilled in the art that the embodiments described herein can be combined with other embodiments.

[0040] In the description of the embodiments of this application, unless otherwise expressly specified and limited, technical terms such as "installation," "connection," "joining," and "fixing" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. For those skilled in the art, the specific meaning of the above terms in the embodiments of this application can be understood according to the specific circumstances.

[0041] Figure 1 This is a schematic diagram of the tool system according to an embodiment of this application. Figure 2 for Figure 1 The diagram shows the simulation results of the modal vibration modes of the cutting tool.

[0042] See Figure 1 This application provides a cutting tool system, including a power vibration damping device 100 and a cutting tool 200. The cutting tool 200 includes a tool holder 210 and a cutting head 220. The axis of the cutting head 220 is set at a preset angle with the axis of the tool holder 210. The power vibration damping device 100 is sleeved on the end of the tool holder 210.

[0043] In this embodiment, the tool 200 is an angle milling head (also known as an angle head), including a cutter head 220, a tool holder 210, and an internal transmission mechanism. The axis of the cutter head 220 and the axis of the tool holder 210 are perpendicular to each other, and the rotational speeds of the tool holder 210 and the cutter head 220 are based on a certain transmission ratio. The tool holder 210 has a large length-to-diameter ratio, making it a weak point in the rigidity of the machining system. For example, the length of the tool holder 210 is 1200 mm, and its diameter is 170 mm, resulting in a length-to-diameter ratio of approximately 7. For workpieces with large length-to-diameter ratio structures such as deep holes and deep cavities, this can easily lead to insufficient end-effector rigidity, causing harmful relative motion between the tool 200 and the workpiece, resulting in severe chatter problems, directly affecting the machining quality, stability, and safety of the workpiece.

[0044] Therefore, in this embodiment of the application, a dynamic vibration damping device 100 with two degrees of freedom is designed for the spatial vibration characteristics of the tool 200. The dynamic vibration damping device 100 is sleeved on the end of the tool holder 210. Then, dynamic modeling, numerical optimization and structural design are carried out on it in sequence. Finally, its vibration damping performance is verified through modal testing and cutting test.

[0045] See Figure 2 This application embodiment performs modal vibration mode simulation analysis on the tool 200, aiming to provide a basis for the arrangement of modal measurement points. The axial direction of the tool holder 210 is taken as the Z-axis, and the plane perpendicular to the axial direction of the tool holder 210 is taken as the XY plane. The two mutually perpendicular directions of the XY plane are the X-axis and the Y-axis, respectively. Fixed boundary conditions are applied to one end of the tool holder 210, while the other end of the tool holder 210 is left free, and the resulting vibration modes are solved.

[0046] To avoid mode shape nodes, the layout of each modal measurement point was determined and a global coordinate system was defined, as follows: Figure 2 As shown. The first measuring point a is set at the connection between the dynamic vibration absorbing device 100 and the tool holder 210, and is used to measure the dynamic characteristics of the tool holder 210 at the installation position of the dynamic vibration absorbing device 100; the second measuring point b is set at the end of the tool head 220, and is used to predict the stability of cutting chatter, so as to further verify the effect of the dynamic vibration absorbing device 100 on improving cutting stability.

[0047] According to simulation results (a) and (b), the first-order mode shape of the tool is bending about its axis and along two orthogonal directions, the X-axis and the Y-axis, respectively. Since the cutting stability is determined by the dynamic characteristics of the tool 200 in the two orthogonal directions, the dynamic vibration damping device 100 should have two translational degrees of freedom to suppress vibrations in the X-axis and Y-axis directions respectively.

[0048] The specific structure of the dynamic vibration absorption device 100 according to the embodiments of this application is described in detail below with reference to the accompanying drawings.

[0049] Figure 3 This is a schematic diagram of the structure of the dynamic vibration absorption device according to an embodiment of this application. Figure 4 for Figure 3 The diagram shows the exploded structure of the dynamic vibration absorption device.

[0050] See Figure 3 and Figure 4 This application provides a dynamic vibration damping device 100, which is sleeved on the end of a vibration shaft. The dynamic vibration damping device 100 includes a base assembly 1, a mass unit 2, a stiffness assembly 3, and a damping unit 4.

[0051] Mass unit 2 is spaced apart from base assembly 1 along the axial direction of the vibration axis.

[0052] The stiffness component 3 includes a plurality of beam members 31 arranged circumferentially along the vibration axis, and the plurality of beam members 31 pass through the base component 1 and the mass unit 2.

[0053] The damping unit 4 is disposed on the side of the mass unit 2 away from the base assembly 1. The damping unit 4 includes a retaining ring 41 and a plurality of damping elements 42. The plurality of damping elements 42 are disposed between the retaining ring 41 and the mass unit 2. At least one damping element 42 forms a first connection with the axis of the vibration shaft, and at least another damping element 42 forms a second connection with the axis of the vibration shaft. The first connection and the second connection are perpendicular to each other in the orthographic projection of the orthographic projection in a plane perpendicular to the axis of the vibration shaft.

[0054] In this embodiment, the vibration shaft can be the handle 210 of the tool 200, and the axial direction of the vibration shaft is the Z-axis. The dynamic vibration absorption device 100 is sleeved on the end of the handle 210. Specifically, the dynamic vibration absorption device 100 includes a base assembly 1, a mass unit 2, a stiffness assembly 3, and a damping unit 4. The vibration shaft is a cylindrical shaft. The base assembly 1, the mass unit 2, and the damping unit 4 are all annular components. The stiffness assembly 3 includes multiple beam members 31 spaced circumferentially along the vibration shaft. The cross-section of the beam members 31 is rectangular, and the number of beam members 31 can be three or four. The multiple beam members 31 pass through the base assembly 1 and the mass unit 2. The damping unit 4 is disposed on the side of the mass unit 2 away from the base assembly 1. The damping unit 4 includes a retaining ring 41 and multiple damping elements 42, which are disposed between the retaining ring 41 and the mass unit 2. The multiple damping elements 42 can be at least two damping elements 42, for example, two damping elements 42 or four damping elements 42. At least one damping element 42 forms a first connection with the axis of the vibration shaft, and at least another damping element 42 forms a second connection with the axis of the vibration shaft. The first or second connection formed between the damping element 42 and the axis of the vibration shaft refers to the first or second connection formed between the center of mass of the damping element 42 and the axis of the vibration shaft. The orthographic projections of the first and second connections in a plane perpendicular to the axis of the vibration shaft are perpendicular to each other, such that at least two damping elements 42 have mutually orthogonal translational degrees of freedom, namely translational degrees of freedom along the X-axis and translational degrees of freedom along the Y-axis, respectively, to suppress the vibration of the tool 200 in the mutually orthogonal X and Y directions.

[0055] Because the dynamic vibration damping device 100 adopts a configuration with two translational degrees of freedom, it can accurately suppress the bending vibration modes of the tool 200 in two orthogonal directions. Compared with a single-degree-of-freedom vibration damper, it can significantly improve the cutting stability of the tool 200.

[0056] According to the power vibration absorption device 100 provided in the embodiments of this application, the vibration energy of the tool holder 210 is transferred to the mass unit 2 through the damping unit 4. The damping unit 4 has at least two damping elements 42 with mutually orthogonal translational degrees of freedom to suppress the vibration of the tool 200 in two mutually orthogonal directions. This can effectively suppress the chatter caused by the structural characteristics of the large aspect ratio structure in the process system during the machining process, and improve the machining accuracy and cutting stability of the workpiece.

[0057] In some embodiments, the retaining ring 41 includes a first retaining ring 411 and a second retaining ring 412 that are disposed around the outer periphery of the vibration shaft and connected to each other. The first retaining ring 411 is provided with a first protrusion 413 extending outward along its own radial direction, and the second retaining ring 412 is provided with a second protrusion 414 extending outward along its own radial direction. The first protrusion 413 and the second protrusion 414 are respectively fixedly connected to the corresponding damping member 42.

[0058] like Figure 3 and Figure 4 As shown, the damping unit 4 is sleeved on the outer periphery of the vibration shaft and fixedly connected to it. To improve the clamping force between the damping unit 4 and the vibration shaft, and to facilitate the assembly of the damping unit 4 onto the outer periphery of the vibration shaft, the retaining ring 41 of the damping unit 4 includes a first retaining ring 411 and a second retaining ring 412 that surround and are connected to each other on the outer periphery of the vibration shaft. The first retaining ring 411 and the second retaining ring 412 are arc-shaped components, and the inner walls of both the first retaining ring 411 and the second retaining ring 412 are semi-circular, with their inner diameters matching the vibration shaft. The first retaining ring 411 is provided with a first protrusion 413 extending outward along its own radial direction, located in the X-axis extension direction. The second retaining ring 412 is provided with a second protrusion 414 extending outward along its own radial direction, located in the Y-axis extension direction. The first protrusion 413 and the second protrusion 414 are fixedly connected to the corresponding damping element 42 to suppress the vibrations of the tool 200 in the mutually orthogonal X and Y directions.

[0059] Optionally, the first clamp 411 and the second clamp 412 are symmetrically arranged, and the number of the first protrusion 413 and the second protrusion 414 is equal, which can be one or two, so as to facilitate the processing and assembly of the damping unit 4. At the same time, symmetrical damping force can be applied to the vibration shaft to reduce the possibility of the dynamic vibration absorption device 100 shifting relative to the vibration shaft.

[0060] In some embodiments, the first protrusion 413 and the second protrusion 414 are respectively provided with grooves (not shown in the figure) on the side facing the mass unit 2. The length direction of the groove is parallel to the axis of the vibration shaft. The damping member 42 is embedded in the groove and contacts the mass unit 2.

[0061] In this embodiment, the mass unit 2 is a circular ring structure, and the inner diameter of the mass unit 2 is smaller than the outer diameter of the groove. This allows the damping element 42 to contact the mass unit 2 and generate damping force after being embedded in the groove. This makes the overall structure of the dynamic vibration absorption device 100 compact and space-saving. In addition, the length direction of the groove is parallel to the axis of the vibration shaft, which allows the damping force generated between the damping element 42 and the mass unit 2 to be applied to the vibration shaft as much as possible, thus improving the vibration suppression effect.

[0062] In addition, by changing the depth of the groove or the height of the damping element 42, the axial displacement of the damping unit 4 along the vibration axis can be adjusted, thereby changing the contact pressure between the damping element 42 and the mass unit 2, thus adjusting the magnitude of the damping force, achieving effective dissipation of vibration energy, and ensuring good vibration suppression performance under different processing conditions.

[0063] In some embodiments, the first clamp 411 is provided with a first positioning ear 415 at both ends along its circumference, and the second clamp 412 is provided with a second positioning ear 416 at both ends along its circumference. The first positioning ear 415 and the second positioning ear 416 are connected by a first fastener 43.

[0064] like Figure 3 and Figure 4 As shown, the first clamp 411 has two first positioning ears 415 respectively provided with first through holes, and the second clamp 412 has two second positioning ears 416 respectively provided with second through holes. The first fastener 43 includes bolts, nuts, washers, etc. The first fastener 43 passes through the first through holes and the second through holes in sequence. By tightening the bolts and nuts, the vibration shaft can be held tightly, reducing the possibility of the dynamic vibration absorption device 100 shifting relative to the vibration shaft.

[0065] In some embodiments, the base assembly 1 includes a first clamping hoop 11 and a second clamping hoop 12 that are disposed around the outer periphery of the vibration shaft and connected to each other. The first clamping hoop 11 is provided with a first mounting portion 13 extending outward along its own radial direction, and the second clamping hoop 12 is provided with a second mounting portion 14 extending outward along its own radial direction. The first mounting portion 13 and the second mounting portion 14 are respectively fixedly connected to one end of the beam member 31 by a fastening assembly 15.

[0066] like Figure 3 and Figure 4As shown, in order to improve the clamping force between the base assembly 1 and the vibration shaft, and to facilitate the assembly of the base assembly 1 to the outer periphery of the vibration shaft, the base assembly 1 includes a first clamping hoop 11 and a second clamping hoop 12 that are arranged around the outer periphery of the vibration shaft and connected to each other. The first clamping hoop 11 and the second clamping hoop 12 are arc-shaped components, and the inner walls of the first clamping hoop 11 and the second clamping hoop 12 are both semi-circular, and their inner diameters are adapted to the vibration shaft. The first clamping hoop 11 is provided with a first mounting portion 13 extending outward along its own radial direction, and the second clamping hoop 12 is provided with a second mounting portion 14 extending outward along its own radial direction. The first mounting portion 13 and the second mounting portion 14 are respectively fixedly connected to one end of the beam component 31 through a fastening assembly 15.

[0067] Optionally, the fastening assembly 15 includes a clamping member, bolts, washers, etc. The clamping member presses one end of the beam member 31 to the first mounting part 13 or the second mounting part 14. The first mounting part 13 or the second mounting part 14 is provided with threaded holes, and the washers and clamping members are connected to the threaded holes by bolts, which facilitates disassembly and assembly.

[0068] In some embodiments, the first clamping hoop 11 is provided with third positioning ears 16 at both ends along its circumference, and the second clamping hoop 12 is provided with fourth positioning ears 17 at both ends along its circumference. The third positioning ears 16 and the fourth positioning ears 17 are connected by a second fastener 18.

[0069] like Figure 3 and Figure 4 As shown, the two third positioning ears 16 of the first clamping hoop 11 are respectively provided with third through holes, and the two fourth positioning ears 17 of the second clamping hoop 12 are respectively provided with fourth through holes. The second fastener 18 includes bolts, nuts, washers, etc. The second fastener 18 passes through the third through holes and the fourth through holes in sequence. By tightening the bolts and nuts, the vibration shaft can be clamped, reducing the possibility of the dynamic vibration absorption device 100 shifting relative to the vibration shaft.

[0070] In some embodiments, the mass unit 2 is provided with a plurality of third mounting portions 21 at intervals along its circumference, and the third mounting portions 21 are fixedly connected to one end of the beam member 31 by fastening components 15.

[0071] like Figure 4 As shown, the mass unit 2 is a circular structure, and multiple third mounting parts 21 are arranged at intervals along its circumference. The third mounting parts 21 are fixedly connected to one end of the beam member 31 through fastening components 15.

[0072] Optionally, the fastening assembly 15 includes a clamping member, bolts, washers, etc. The clamping member is arranged in a "U" shape and clamps the other end of the beam member 31 to the third mounting part 21. The third mounting part 21 is provided with a threaded hole, and the washer and clamping member are connected to the threaded hole through the bolt, which facilitates disassembly and assembly.

[0073] Because the fastening assembly 15 is easy to disassemble and assemble, the position of the mass unit 2 on the beam member 31 can be quickly adjusted. By moving the position of the mass unit 2 on the beam member 31, the equivalent suspension length of the beam member 31 can be changed, thereby achieving continuous adjustment of stiffness and thus changing the stiffness and natural frequency of the dynamic vibration absorption device 100 to adapt to the frequency adjustment requirements under different working conditions.

[0074] In some embodiments, the number of damping elements 42 is four, and the four damping elements 42 are arranged in a centrally symmetrical manner with respect to the axis of the vibration shaft; and / or, the number of beam members 31 is four, and the four beam members 31 are arranged in a centrally symmetrical manner with respect to the axis of the vibration shaft.

[0075] like Figure 4 As shown, the first clamp 411 has two first protrusions 413, and the second clamp 412 has two second protrusions 414. One first protrusion 413 and one second protrusion 414 are arranged in a straight line and parallel to the X-axis, while the other first protrusion 413 and the other second protrusion 414 are arranged in a straight line and parallel to the Y-axis. This allows symmetrical damping force to be applied to the vibration shaft, reducing the possibility of the dynamic vibration absorption device 100 shifting relative to the vibration shaft.

[0076] The number of beam members 31 can be four. The four beam members 31 are arranged in a centrally symmetrical manner with respect to the axis of vibration. Each beam member 31 is correspondingly arranged with a damping element 42, thereby effectively suppressing vibration in the X or Y direction.

[0077] In some embodiments, the mass unit 2 is made of steel, the base assembly 1, the stiffness assembly 3 and the retaining ring 41 are all made of aluminum alloy, and the damping component 42 is made of rubber or granular stone.

[0078] Optionally, the mass unit 2 is made of 45# steel, while the base assembly 1, stiffness assembly 3, and retaining ring 41 are all made of aluminum alloy. The damping component 42 is made of a material with a high coefficient of friction, such as, but not limited to, rubber or granular stone. Because the density of the mass unit 2 is greater than that of the base assembly 1, stiffness assembly 3, and retaining ring 41, the deformation of the mass unit 2 under natural gravity is smaller, and it will not cause structural interference with other components.

[0079] Assuming the effective overhang of the tool holder 210 of the cutting tool 200 is 150mm, and the cross-section of the beam member 31 is square with a side length of 8mm, a dynamic model of the cutting tool without the attached dynamic vibration damping device 100 is established for finite element simulation analysis. Under natural gravity, the maximum deformation displacement of the dynamic vibration damping device 100 is 0.3mm, ensuring that it does not interfere with the cutting head 220 during the cutting process. Simultaneously, the maximum stress of the dynamic vibration damping device 100 is located at the connection between the beam member 31 and the mass element 2, with a stress value of 32MPa. Taking a safety factor of 3, the maximum stress is far below the allowable stress, ensuring the structural reliability of the dynamic vibration damping device 100 during operation.

[0080] Figure 5 This is a schematic diagram of the simulation results of the main vibration mode of the dynamic vibration absorption device according to an embodiment of this application.

[0081] like Figure 5 As shown, to verify the effectiveness of the structural design of the dynamic vibration absorption device 100, this embodiment of the application establishes a dynamic model of the tool system of the tool-dynamic vibration absorption device based on the measured dynamic characteristics of the tool 200. On this basis, through numerical optimization, the optimal dynamic parameters of the dynamic vibration absorption device 100 are solved, and the optimal frequency of the target mode of the tool 200 is found to be 34.77Hz. For the vibration mode characteristics of the tool 200, the configuration of the dynamic vibration absorption device 100 is designed using the spectrogram method, and finite element simulation analysis is performed on the prototype. Finally, modal tests are conducted.

[0082] By changing the position of the moving mass element 2 on the beam member 31 to alter the equivalent overhang of the beam member 31, the frequency tuning capability of the dynamic vibration absorption device 100 can be simulated, and the results are shown in Table 1. When the effective overhang of the beam member 31 is 180 mm, the vibration frequency of the dynamic vibration absorption device 100 is close to the optimal frequency of 37.2 Hz; when the effective overhang of the beam member 31 is the maximum value of 300 mm, the vibration frequency of the dynamic vibration absorption device 100 reaches the minimum value of 17.6 Hz. When the equivalent overhang of the beam member 31 decreases to 85 mm, the vibration frequency of the dynamic vibration absorption device 100 increases to its maximum value of 107.9 Hz. It can be seen that the tuning range of the dynamic vibration absorption device 100 can cover the optimal frequency of 34.77 Hz for suppressing the target mode of the tool 200.

[0083] Table 1

[0084]

[0085] Because the tool system with the added dynamic vibration damping device 100 has structural symmetry, its dynamic characteristics along the two orthogonal directions X and Y are similar. Therefore, this embodiment only tests the origin frequency response function along the Y-axis at the first measuring point a and the second measuring point b. The first measuring point a is located at the connection between the dynamic vibration damping device 100 and the tool holder 210, used to measure the dynamic characteristics of the tool holder 210 at the mounting position of the dynamic vibration damping device 100. The second measuring point b is located at the end of the tool tip 220, used to predict the stability of cutting chatter, to further verify the effect of the dynamic vibration damping device 100 on improving cutting stability.

[0086] Figure 6 for Figure 2 The diagram shows the frequency response function measurement results at the first measuring point of the cutting tool. Figure 7 for Figure 2 The diagram shows the frequency response function measurement results at the second measuring point of the cutting tool.

[0087] Based on the measurement results of the frequency response function, the stiffness and damping unit 4 of the dynamic vibration absorption device 100 were continuously tuned until the parameters of the dynamic vibration absorption device 100 reached their optimal values. After the dynamic vibration absorption device 100 was tuned to its optimal dynamic parameters, the measured frequency response function of the tool 200 was as follows: Figure 6 and Figure 7 As shown.

[0088] like Figure 6 As shown, before and after the addition of the dynamic vibration damping device 100, the peak values ​​of the frequency response function at the first measuring point a are 4.81 × 10⁻⁶ g / N and 3.01 × 10⁻⁶ g / N, respectively, with an amplitude reduction of approximately 37.5%. Figure 7 As shown, the peak frequency response function of the second measuring point b before the auxiliary dynamic vibration absorption device 100 is 1.10×10-5 g / N, while the peak frequency response function after the auxiliary dynamic vibration absorption device 100 is 2.92×10-6 g / N, a decrease of approximately 73.5%. This demonstrates that the dynamic vibration absorption device 100 can effectively suppress the main vibration mode of the tool.

[0089] Figure 8 To adopt Figure 1 The image shows a comparison of the surface quality of a workpiece cut by a tool system and a tool without a power vibration damping device.

[0090] To verify the chatter suppression effect of the dynamic vibration absorption device 100, a cutting test was conducted on the workpiece. The workpiece was a rectangular blank made of aluminum alloy. Based on the frequency response functions of the three orthogonal directions measured at the second measuring point b in the modal test, the chatter stability during the cutting process was predicted using the zero-order frequency domain method. The proposed working condition was slot milling. The tool 200 had a cutter head 220 made of cemented carbide with 2 teeth. The cutting path was fed along the Y-axis, and the feed per tooth was fz = 0.11 mm.

[0091] Based on the above results, to facilitate observation of the actual cutting vibration suppression effect of the dynamic vibration absorption device 100, experiments were conducted at speeds of 600 r / min and 1000 r / min, and the selected cutting parameters are shown in Table 2. The workpiece surface before and after the addition of the dynamic vibration absorption device 100 is shown in Table 2. Figure 8 As shown in the figure, cutting parameters #1, #2, and #3 respectively show the chatter marks on the workpiece surface before and after the auxiliary power vibration damping device 100 is applied when the spindle speed of the tool holder 210 is 600 r / min. It can be seen that the depth of cut increases from 0.5 mm before the auxiliary device to 1.1 mm after the auxiliary device is applied, the chatter mark elimination effect is obvious, the stable depth of cut increases by 120%, and chatter is effectively suppressed.

[0092] Similarly, cutting parameters #4, #5, and #6 respectively show the vibration marks on the workpiece surface before and after the additional power vibration damping device 100 when the spindle speed of the tool holder 210 is 1000 r / min. The depth of cut increases from 0.4 mm before the addition to 1.6 mm after the addition, the vibration mark elimination effect is more obvious, and the stable depth of cut increases by 300%.

[0093] Table 2

[0094]

[0095] Therefore, in this embodiment of the tool system, a dynamic vibration damping device 100 as described above is added to the end of the tool holder 210 of the tool 200. Based on the measured dynamic characteristics of the tool system, a dynamic model of the tool-dynamic vibration damping device is established. On this basis, the optimal dynamic parameters of the damper are solved through numerical optimization. For the vibration mode characteristics of the tool, the configuration of the dynamic vibration damping device 100 is designed using the graphical method, and finite element simulation is performed on the prototype. Finally, modal tests and cutting tests are conducted to verify its effectiveness. The test results show that after adding the dynamic vibration damping device 100, the peak value of the frequency response function at the tool end is reduced by 73.5%, while significantly increasing the stable depth of cut, effectively suppressing chatter, and improving the machining accuracy and stability of the workpiece.

[0096] The above description is merely a preferred embodiment of this application, but the scope of protection of this application is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in this application should be included within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims.

Claims

1. A dynamic vibration damping device, used for being sleeved on the end of a vibrating shaft, characterized in that, The dynamic vibration absorption device includes: Base assembly; Mass units are spaced apart from the base assembly along the axial direction of the vibration axis; A stiffness assembly includes a plurality of beam members spaced circumferentially along the vibration axis. The beam members pass through a base assembly and a mass unit. The base assembly includes a first clamping hoop and a second clamping hoop, which are arranged around the outer periphery of the vibration axis and interconnected. The first clamping hoop has a first mounting portion extending radially outward, and the second clamping hoop has a second mounting portion extending radially outward. The first and second mounting portions are respectively fixedly connected to one end of the beam members by fastening assemblies. The equivalent overhang of the beam members is adjusted by moving the position of the mass unit on the beam members. A damping unit is disposed on the side of the mass unit away from the base assembly. The damping unit includes a retaining ring and a plurality of damping elements. The plurality of damping elements are disposed between the retaining ring and the mass unit. At least one of the damping elements forms a first connection with the axis of the vibration shaft, and at least another damping element forms a second connection with the axis of the vibration shaft. The first connection and the second connection are perpendicular to each other in the orthogonal projection in a plane perpendicular to the axis of the vibration shaft. The at least two damping elements are respectively disposed in mutually orthogonal directions to apply damping to the bending vibrations of the vibration shaft in two orthogonal directions.

2. The dynamic vibration absorption device according to claim 1, characterized in that, The retaining ring includes a first retaining ring and a second retaining ring that are arranged around the outer periphery of the vibration shaft and connected to each other. The first retaining ring is provided with a first protrusion extending outward along its own radial direction, and the second retaining ring is provided with a second protrusion extending outward along its own radial direction. The first protrusion and the second protrusion are respectively fixedly connected to the corresponding damping element.

3. The dynamic vibration absorption device according to claim 2, characterized in that, The first protrusion and the second protrusion are respectively provided with grooves on the side facing the mass unit. The length direction of the grooves is parallel to the axis of the vibration shaft. The damping element is embedded in the grooves and contacts the mass unit.

4. The dynamic vibration absorption device according to claim 2, characterized in that, The first clamp has a first positioning ear at each end along its circumference, and the second clamp has a second positioning ear at each end along its circumference. The first positioning ear and the second positioning ear are connected by a first fastener.

5. The dynamic vibration absorption device according to claim 1, characterized in that, The first clamping hoop has a third positioning ear at each end along its circumference, and the second clamping hoop has a fourth positioning ear at each end along its circumference. The third positioning ear and the fourth positioning ear are connected by a second fastener.

6. The dynamic vibration absorption device according to claim 1, characterized in that, The mass unit is provided with a plurality of third mounting parts at intervals along its circumference, and the third mounting parts are fixedly connected to one end of the beam member by fastening components.

7. The dynamic vibration absorption device according to any one of claims 1 to 6, characterized in that, The number of damping elements is four, and the four damping elements are arranged in a centrally symmetrical manner with respect to the axis of the vibration shaft; And / or, the number of beam members is four, and the four beam members are arranged in a centrally symmetrical manner with respect to the axis of the vibration shaft.

8. The dynamic vibration absorption device according to claim 1, characterized in that, The mass unit is made of steel, the base assembly, the stiffness assembly and the retaining ring are all made of aluminum alloy, and the damping component is made of rubber or granular stone.

9. A cutting tool system, characterized in that, include: A cutting tool, including a handle and a cutting head, wherein the axis of the cutting head is set at a preset angle with the axis of the handle; and The power vibration damping device as described in any one of claims 1 to 8, wherein the power vibration damping device is sleeved on the end of the tool holder.

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