Cutting tool and cutting machining device

Abstract

A cutting tool is a cutting tool that rotates around an axis, and has a main body portion, a cutting insert, and a plurality of vibration-proof members. The main body portion has an inner peripheral surface and an outer peripheral surface on the opposite side of the inner peripheral surface. The cutting insert is attached to at least either one of the inner peripheral surface and the outer peripheral surface. The plurality of vibration-proof members are each provided to the main body portion. The plurality of vibration-proof members each include a counterweight member made of a material having a large specific gravity compared with a material constituting the main body portion.

Description

TECHNICAL FIELD

[0001] The present application relates to a cutting tool and a cutting processing device. This application claims priority based on Japanese Patent Application No. 2020-137877 filed on August 18, 2020. The entire written content described in the Japanese Patent Application is incorporated by reference into the present specification. BACKGROUND

[0002] A pin milling cutter for processing a crank shaft is disclosed in Japanese Patent Application Publication No. 2007-210036 (Patent Literature 1). The pin milling cutter has a blade, a main body portion, and an adapter. The blade is installed at the inner peripheral side of the main body portion. The adapter is installed at the outer peripheral side of the main body portion.

[0003] Patent Literature 1: Japanese Patent Application Publication No. 2007-210036 SUMMARY

[0004] The cutting tool according to the present application is a cutting tool that rotates around an axis, and has a main body portion, a cutting blade, and a plurality of vibration-proof members. The main body portion has an inner peripheral surface and an outer peripheral surface. The cutting blade is installed at at least either one of the inner peripheral surface and the outer peripheral surface. The plurality of vibration-proof members are each provided to the main body portion. The plurality of vibration-proof members each include a counterweight member that is made of a material having a large specific gravity compared to a material that constitutes the main body portion. BRIEF DESCRIPTION OF DRAWINGS

[0005] Figure 1 is a schematic plan view that shows the structure of the cutting tool according to the first embodiment.

[0006] Figure 2 is a schematic side view that shows the structure of the cutting tool according to the first embodiment.

[0007] Figure 3 is a schematic plan view that shows the structure of the counterweight member of the cutting tool according to the first embodiment.

[0008] Figure 4 is a schematic plan view that shows the structure of the insertion member.

[0009] Figure 5 is a schematic cross-sectional view that shows a state in which the vibration-proof member is installed to the main body portion.

[0010] Figure 6 is a cross-sectional view along the line VI-VI of Figure 5 .

[0011] Figure 7 is a schematic plan view that shows the structure of the cutting processing device according to the second embodiment.

[0012] Figure 8is a schematic plan view showing the structure of the cutting tool according to the third embodiment.

[0013] Figure 9 is a schematic plan view showing the structure of the counterweight member of the cutting tool according to the third embodiment.

[0014] Figure 10 is a schematic plan view showing the structure of the cutting tool according to the fourth embodiment.

[0015] Figure 11 is a schematic side view showing the vibration measurement method.

[0016] Figure 12 is a graph showing the vibration measurement results.

[0017] Figure 13 is a schematic view showing the structure of the thrust surface and the flank surface of the crankshaft.

[0018] Figure 14 is a graph showing the surface roughness measurement results. DETAILED DESCRIPTION

[0019] [Problems to be Solved by the Invention]

[0020] In the pin miller cutter, in the recess formed in the adapter, a filler material having a larger specific gravity than the material forming the adapter is filled. Therefore, vibration occurring due to contact of the insert with the cut material is conducted to the adapter via the main body. Since the main body is present between the adapter and the insert, vibration of the vibration suppression object cannot be sufficiently captured at the filler material provided in the adapter. Therefore, vibration during cutting processing cannot be sufficiently attenuated.

[0021] An object of the present application is to provide a cutting tool and a cutting processing apparatus capable of attenuating vibration during cutting processing.

[0022] [Effects of the Invention]

[0023] According to the present application, a cutting tool and a cutting processing apparatus capable of attenuating vibration during cutting processing can be provided.

[0024] [Explanation of Embodiments of the Invention]

[0025] First, an embodiment of the present application will be explained.

[0026] (1) The cutting tool 100 according to the present application is a cutting tool 100 that rotates around an axis A, and has a main body 10, a cutting insert 7, and a plurality of vibration-proof members 8. The main body 10 has an inner peripheral surface 4 and an outer peripheral surface 3. The cutting insert 7 is attached to at least either one of the inner peripheral surface 4 and the outer peripheral surface 3. The plurality of vibration-proof members 8 are each provided to the main body 10. The plurality of vibration-proof members 8 each include a counterweight member 20 made of a material having a larger specific gravity than a material that constitutes the main body 10.

[0027] According to the cutting tool 100 according to the above (1), the plurality of vibration-proof members 8 are each provided to the main body 10. The cutting insert 7 is attached to the main body 10. Therefore, vibration that occurs when the cutting insert 7 contacts a workpiece is attenuated by the plurality of vibration-proof members 8 each provided to the main body 10. Thus, compared with the cutting tool 100 in which the vibration-proof members 8 are provided to a holder, vibration during cutting can be attenuated more efficiently.

[0028] (2) In the cutting tool 100 according to the above (1), when viewed in the direction of the axis A, the plurality of vibration-proof members 8 can each be disposed on an imaginary circle B centered on the axis A. Thus, the distance between the axis A and each of the plurality of vibration-proof members 8 is equal, and therefore vibration during cutting can be attenuated more efficiently.

[0029] (3) In the cutting tool 100 according to the above (2), when viewed in the direction of the axis A, the plurality of vibration-proof members 8 can each be disposed at equal intervals in the circumferential direction of the imaginary circle B. Thus, vibration during cutting can be attenuated equally in the circumferential direction.

[0030] (4) In the cutting tool 100 according to any one of the above (1) to (3), a hollow portion 9 surrounded by an inner wall surface 6 can be provided to the main body 10. The counterweight member 20 can be disposed in the hollow portion 9 in a state separated from the inner wall surface 6. The counterweight member 20 is separated from the inner wall surface 6, and therefore the counterweight member 20 is movable in the hollow portion 9. Thus, the counterweight member 20 vibrates in an opposite phase to vibration of the main body 10. Therefore, the vibration-proof member 8 functions as a dynamic vibration absorber. Thus, compared with a case where the counterweight member 20 contacts the inner wall surface 6, vibration during cutting can be attenuated further.

[0031] (5) In the cutting tool 100 according to the above (4), the counterweight member 20 can be provided with a through-hole 24. Each of the plurality of vibration-proof members 8 can include a pin member 12 that penetrates the through-hole 24 and is attached to the inner wall surface 6, and an elastic member 13 that surrounds the pin member 12 and contacts the counterweight member 20 inside the through-hole 24. The counterweight member 20 can attenuate vibration by friction between the counterweight member 20 and the elastic member 13 and friction between the elastic member 13 and the pin member 12. Thus, vibration can be efficiently attenuated not only with respect to radial vibration but also with respect to axial and circumferential vibration.

[0032] (6) In the cutting tool 100 according to any one of the above (1) to (5), the counterweight member 20 can have a racetrack shape when viewed in the direction of the axis A. Thus, the counterweight member 20 can be increased in size compared to a case where the counterweight member 20 has a linear shape. As a result, vibration during cutting can be further attenuated.

[0033] (7) In the cutting tool 100 according to the above (3), the main body 10 can be provided with a hollow portion 9 surrounded by the inner wall surface 6. The counterweight member 20 can be disposed in the hollow portion 9 in a state separated from the inner wall surface 6. The counterweight member 20 can be provided with a through-hole 24. Each of the plurality of vibration-proof members 8 can include a pin member 12 that penetrates the through-hole 24 and is attached to the inner wall surface 6, and an elastic member 13 that surrounds the pin member 12 and contacts the counterweight member 20 inside the through-hole 24. The counterweight member 20 can have a racetrack shape when viewed in the direction of the axis A.

[0034] According to the cutting tool 100 according to the above (7), the counterweight member 20 is separated from the inner wall surface 6, and thus the counterweight member 20 can move in the hollow portion 9. Thus, the counterweight member 20 vibrates in an anti-phase with respect to vibration of the main body 10. Thus, the vibration-proof member 8 functions as a dynamic vibration absorber. Thus, vibration during cutting can be further attenuated compared to a case where the counterweight member 20 contacts the inner wall surface 6. In addition, the counterweight member 20 can attenuate vibration by friction between the counterweight member 20 and the elastic member 13 and friction between the elastic member 13 and the pin member 12. Thus, vibration can be efficiently attenuated not only with respect to radial vibration but also with respect to axial and circumferential vibration. Furthermore, in a case where the counterweight member 20 has a racetrack shape when viewed in the direction of the axis A, the counterweight member 20 can be increased in size compared to a case where the counterweight member 20 has a linear shape. As a result, vibration during cutting can be further attenuated.

[0035] (8) The cutting tool 100 according to any one of (1) to (7) and the holder 40 that holds the main body 10.

[0036] [Details of Embodiments of the Invention]

[0037] Next, details of embodiments of the invention will be described based on the drawings. Furthermore, the same reference numerals are assigned to the same or equivalent portions in the following drawings, and the description thereof will not be repeated.

[0038] (First Embodiment)

[0039] First, the structure of the cutting tool 100 according to the first embodiment will be described.

[0040] Figure 1 is a schematic plan view showing the structure of the cutting tool according to the first embodiment. As shown in Figure 1 the cutting tool 100 according to the first embodiment is, for example, a pin miller cutter. The cutting tool 100 according to the first embodiment is a cutting tool 100 that rotates around an axis A, and mainly has a main body 10, a plurality of cutting inserts 7, and a plurality of anti-vibration members 8. The main body 10 has a ring-like shape. The main body 10 has an inner peripheral surface 4 and an outer peripheral surface 3. The inner peripheral surface 4 and the outer peripheral surface 3 each surround the axis A.

[0041] The cutting insert 7 is mounted to at least either one of the inner peripheral surface 4 and the outer peripheral surface 3. In the cutting tool 100 according to the first embodiment, the cutting insert 7 is mounted to the inner peripheral surface 4 of the main body 10. The cutting insert 7 is exposed at the inner peripheral surface 4. The number of the cutting insert 7 is not particularly limited, and is, for example, 36. The cutting insert 7 can be arranged at equal intervals in the circumferential direction of the main body 10.

[0042] The cutting insert 7 has, for example, a longitudinal insert 7a and a transverse insert 7b. The longitudinal insert 7a is arranged, for example, with the length direction of the rake face in the radial direction of the main body 10. The transverse insert 7b is arranged, for example, with the length direction of the rake face in the axial direction of the main body 10. The axial direction is a direction parallel to the axis A. The radial direction is a direction perpendicular to the axis A.

[0043] Figure 2 is a schematic side view showing the structure of the cutting tool according to the first embodiment. The main body 10 has a first main surface 1 and a second main surface 2. The second main surface 2 is opposite to the first main surface 1. The first main surface 1 is continuous with each of the outer peripheral surface 3 and the inner peripheral surface 4. Likewise, the second main surface 2 is continuous with each of the outer peripheral surface 3 and the inner peripheral surface 4. The second main surface 2 is substantially parallel to the first main surface 1. Each of the first main surface 1 and the second main surface 2 is substantially perpendicular to the axis A.

[0044] As shown in FIG. 1, a portion (cutting edge) of the longitudinal blade 7a can protrude from each of the first main surface 1 and the second main surface 2 in a direction parallel to the axis A when viewed from a direction perpendicular to the axis A. Similarly, a portion (cutting edge) of the transverse blade 7b can protrude from each of the first main surface 1 and the second main surface 2 in a direction parallel to the axis A when viewed from a direction perpendicular to the axis A. The thickness T of the main body portion 10 in the direction parallel to the axis A is, for example, 17 mm or more and 30 mm or less. Figure 2 As shown in FIG. 1, a portion (cutting edge) of the longitudinal blade 7a can protrude from each of the first main surface 1 and the second main surface 2 in a direction parallel to the axis A when viewed from a direction perpendicular to the axis A. Similarly, a portion (cutting edge) of the transverse blade 7b can protrude from each of the first main surface 1 and the second main surface 2 in a direction parallel to the axis A when viewed from a direction perpendicular to the axis A. The thickness T of the main body portion 10 in the direction parallel to the axis A is, for example, 17 mm or more and 30 mm or less.

[0045] As shown in FIG. 1, a portion (cutting edge) of the longitudinal blade 7a can protrude from each of the first main surface 1 and the second main surface 2 in a direction parallel to the axis A when viewed from a direction perpendicular to the axis A. Similarly, a portion (cutting edge) of the transverse blade 7b can protrude from each of the first main surface 1 and the second main surface 2 in a direction parallel to the axis A when viewed from a direction perpendicular to the axis A. The thickness T of the main body portion 10 in the direction parallel to the axis A is, for example, 17 mm or more and 30 mm or less. Figure 1 As shown in FIG. 1, a portion (cutting edge) of the longitudinal blade 7a can protrude from each of the first main surface 1 and the second main surface 2 in a direction parallel to the axis A when viewed from a direction perpendicular to the axis A. Similarly, a portion (cutting edge) of the transverse blade 7b can protrude from each of the first main surface 1 and the second main surface 2 in a direction parallel to the axis A when viewed from a direction perpendicular to the axis A. The thickness T of the main body portion 10 in the direction parallel to the axis A is, for example, 17 mm or more and 30 mm or less. Figure 2 As shown in FIG. 1, a portion (cutting edge) of the longitudinal blade 7a can protrude from each of the first main surface 1 and the second main surface 2 in a direction parallel to the axis A when viewed from a direction perpendicular to the axis A. Similarly, a portion (cutting edge) of the transverse blade 7b can protrude from each of the first main surface 1 and the second main surface 2 in a direction parallel to the axis A when viewed from a direction perpendicular to the axis A. The thickness T of the main body portion 10 in the direction parallel to the axis A is, for example, 17 mm or more and 30 mm or less.

[0046] As shown in FIG. 1, a portion (cutting edge) of the longitudinal blade 7a can protrude from each of the first main surface 1 and the second main surface 2 in a direction parallel to the axis A when viewed from a direction perpendicular to the axis A. Similarly, a portion (cutting edge) of the transverse blade 7b can protrude from each of the first main surface 1 and the second main surface 2 in a direction parallel to the axis A when viewed from a direction perpendicular to the axis A. The thickness T of the main body portion 10 in the direction parallel to the axis A is, for example, 17 mm or more and 30 mm or less. Figure 1 As shown in FIG. 1, a portion (cutting edge) of the longitudinal blade 7a can protrude from each of the first main surface 1 and the second main surface 2 in a direction parallel to the axis A when viewed from a direction perpendicular to the axis A. Similarly, a portion (cutting edge) of the transverse blade 7b can protrude from each of the first main surface 1 and the second main surface 2 in a direction parallel to the axis A when viewed from a direction perpendicular to the axis A. The thickness T of the main body portion 10 in the direction parallel to the axis A is, for example, 17 mm or more and 30 mm or less. Figure 1 As shown in FIG. 1, a portion (cutting edge) of the longitudinal blade 7a can protrude from each of the first main surface 1 and the second main surface 2 in a direction parallel to the axis A when viewed from a direction perpendicular to the axis A. Similarly, a portion (cutting edge) of the transverse blade 7b can protrude from each of the first main surface 1 and the second main surface 2 in a direction parallel to the axis A when viewed from a direction perpendicular to the axis A. The thickness T of the main body portion 10 in the direction parallel to the axis A is, for example, 17 mm or more and 30 mm or less.

[0047] Figure 3 is a schematic plan view showing the structure of the counterweight member of the cutting tool according to the first embodiment. Each of the plurality of vibration-proof members 8 includes a counterweight member 20. The counterweight member 20 is made of a material having a large specific gravity compared to the material constituting the main body portion 10. The material constituting the main body portion 10 is, for example, cemented carbide. Cemented carbide is sintered tungsten carbide (WC) with cobalt (Co) as a binder. The specific gravity of cemented carbide is, for example, 13 g / cm 3 and 15 g / cm 3 and 15 g / cm

[0048] The material constituting the counterweight component 20 is, for example, a tungsten alloy with tungsten as the main component. The tungsten alloy may, for example, contain tungsten, nickel, and copper. Alternatively, the tungsten alloy may contain tungsten, nickel, and iron. The specific gravity of the tungsten alloy is, for example, greater than 13 g / cm³. 3 And 18.3g / cm 3 the following.

[0049] like Figure 3 As shown, when viewed along axis A, the counterweight component 20 can have a track shape. The track shape can be a shape enclosed by an arc that is part of a sector and has a larger radius of curvature than an imaginary circle B centered on axis A, an arc with a central angle approximately equal to that arc and a smaller radius of curvature than the imaginary circle B centered on axis A, and a curve connecting the ends of the former arc and the ends of the latter arc. This curve can be an arc. The curved portion of the track shape can be a line segment instead of a curve. The longitudinal axis of the track shape can be a straight line. The track shape can also be a curved track shape, with the longitudinal axis of the track shape along a portion of a circumference. Preferably, the longitudinal axis of the track shape is along an imaginary circle B centered on axis A. The track shape can be an elliptical track shape. The counterweight component 20 has a first end face 21, a second end face 22, and a third end face 23. A through hole 24 is provided in the counterweight component 20. The through hole 24 is open on both the first end face 21 and the second end face 22. The number of through holes 24 is not particularly limited, for example, two.

[0050] The third end face 23 connects the first end face 21 and the second end face 22. For example... Figure 3 As shown, when viewed along axis A, the first end face 21 and the third end face 23 are each a curved surface that bulges outwards. The second end face 22 is a curved surface that bulges inwards. The radius of curvature of the second end face 22 can be greater than the radius of curvature of the third end face 23. The radius of curvature of the first end face 21 can be greater than the radius of curvature of the second end face 22.

[0051] Figure 4 This is a top view schematic diagram showing the structure of the insert components. Multiple vibration damping components 8 each have an insert component 15. The insert component 15, for example, has a pin component 12, an elastic component 13, and a positioner 14. The pin component 12 is a rod-shaped component. The pin component 12 is, for example, made of metal. The positioner 14 is a cylindrical component. The positioner 14 is, for example, made of resin. The pin component 12 passes through the hollow portion of the positioner 14. The elastic component 13 is a ring-shaped component. The elastic component 13 is, for example, an O-ring. The elastic component 13 is, for example, made of rubber.

[0052] The number of the elastic members 13 is not particularly limited, and for example, two are provided. The pin member 12 penetrates the hollow portion of the elastic member 13. Along the length direction of the pin member 12, the elastic member 13, the positioner 14, and the elastic member 13 are provided in this order. From another viewpoint, the positioner 14 is sandwiched by the two elastic members 13, for example. Further, the length direction of the pin member 12 corresponds to the radial direction of the main body portion 10.

[0053] In the axial direction of the pin member 12, the length of the pin member 12 is greater than the sum of the thickness of two times the thickness of the elastic member 13 and the thickness of the positioner 14. In the axial direction of the pin member 12, the thickness of the elastic member 13 can be smaller than the thickness of the positioner 14. The diameter of the pin member 12 is smaller than the outer diameter of the elastic member 13. The diameter of the pin member 12 is smaller than the outer diameter of the positioner 14. The outer diameter of the positioner 14 can be smaller than the outer diameter of the elastic member 13. The thickness of the elastic member 13 can be smaller than the outer diameter of the elastic member 13.

[0054] Figure 5 is a cross-sectional view showing a state in which the vibration-proof member is attached to the main body portion. Figure 5 The cross section shown is a cross section perpendicular to the axis A. As Figure 5 As shown, the main body portion 10 is provided with a hollow portion 9. The hollow portion 9 is surrounded by the inner wall surface 6. The counterweight member 20 can be disposed in the hollow portion 9 in a state separated from the inner wall surface 6. The hollow portion 9 penetrates the main body portion 10 in a direction parallel to the axis A. The hollow portion 9 is open at each of the first main surface 1 and the second main surface 2.

[0055] The inner wall surface 6 is provided with a first recessed portion 31 and a second recessed portion 32, for example. The first recessed portion 31 is located on the outer peripheral surface side with respect to the pin member 12. One end of the pin member 12 is disposed in the first recessed portion 31. The first recessed portion 31 can be open at the outer peripheral surface 3. The second recessed portion 32 is located on the inner peripheral surface side with respect to the pin member 12. The other end of the pin member 12 is disposed in the second recessed portion 32. The first recessed portion 31 and the second recessed portion 32 each extend in the radial direction of the main body portion 10, for example. The cutting tool 100 can have a fixing member 16. The fixing member 16 is disposed in the first recessed portion 31. The fixing member 16 urges the pin member 12 against the main body portion 10.

[0056] As Figure 5 shown, the through hole 24 of the counterweight member 20 is disposed so as to communicate with each of the first recessed portion 31 and the second recessed portion 32. The pin member 12 penetrates the through hole 24. The pin member 12 is attached to the inner wall surface 6 of the hollow portion 9. The elastic member 13 surrounds the pin member 12. The elastic member 13 is in contact with the counterweight member 20 inside the through hole 24. The elastic member 13 is in contact with the inner surface of the through hole 24 and the pin member 12 in the circumferential direction of the main body portion 10. The elastic member 13 is in contact with the inner wall surface 6 and the positioner 14 in the length direction of the pin member 12.

[0057] The first end face 21 and the second end face 22 each face the inner wall surface 6 of the hollow portion 9 in the radial direction of the main body 10. In the radial direction of the main body 10, the first end face 21 is located between the second end face 22 and the outer peripheral surface 3. In the radial direction of the main body 10, the second end face 22 is located between the first end face 21 and the inner peripheral surface 4. The third end face 23 faces the inner wall surface 6 of the hollow portion 9 in the circumferential direction of the main body 10.

[0058] Figure 6 It is along Figure 5 A cross-sectional view of line VI-VI. Figure 6 The cross-section shown is parallel to axis A. For example... Figure 6 As shown, in a direction parallel to axis A, the elastic member 13 is connected to both the pin member 12 and the counterweight member 20. In the same direction, the counterweight member 20 is housed within a hollow portion 9 formed by the inner wall surface 6, and preferably does not extend from the hollow portion 9. Alternatively, in a direction parallel to axis A, the counterweight member 20 is located between the first main surface 1 and the second main surface 2.

[0059] The number of pins 12 in one vibration damping component 8 is not particularly limited, for example, it can be two or more. When there is only one pin 12, the counterweight component 20 sometimes rotates around the pin 12, and a part of the counterweight component 20 protrudes from the hollow part 9. By setting the number of pins 12 to two or more, it is possible to prevent the counterweight component 20 from protruding from the hollow part 9.

[0060] (Second Implementation)

[0061] Next, the structure of the cutting apparatus 200 according to the second embodiment will be described.

[0062] Figure 7 This is a top view schematic diagram showing the structure of the cutting processing apparatus according to the second embodiment. (Example) Figure 7 As shown, the cutting apparatus 200 according to the second embodiment mainly includes the cutting tool 100, the connector 40, and the mounting member 50 according to the first embodiment. The cutting tool 100 has a main body 10, a cutting insert 7, and a vibration damping member 8. The main body 10 is mounted on the connector 40. The connector 40 holds the main body 10. Figure 7 As shown, when viewed in a direction parallel to axis A, the connector 40 surrounds the main body 10. Alternatively, the cutting tool 100 described later in the third embodiment or the fourth embodiment may be used instead of the cutting tool 100 described in the first embodiment.

[0063] like Figure 7As shown, the connector 40 is, for example, an annular component. A plurality of mounting protrusions 41 are provided on the inner circumferential side of the connector 40. Each of the plurality of mounting protrusions 41 of the connector 40 is inserted into a plurality of mounting recesses 5 provided on the main body 10. Alternatively, each of the plurality of mounting protrusions 41 of the connector 40 engages with a plurality of mounting recesses 5 provided on the main body 10. The main body 10 is fixed to the connector 40 by a mounting member 50.

[0064] like Figure 7 As shown, the connector 40 may be provided with a plurality of mounting holes 42. The plurality of mounting holes 42 are mounted on an external rotating device (not shown). The rotating device rotates, thereby rotating the connector 40. The connector 40 rotates, thereby rotating the cutting tool 100 in the rotation direction C. The rotational force of the rotating device is transmitted to the cutting tool 100 via the connector 40. The rotation direction C of the cutting tool 100 corresponds to the circumferential direction of the main body 10.

[0065] (Third Implementation)

[0066] Next, the structure of the cutting tool 100 according to the third embodiment will be described. The cutting tool 100 according to the third embodiment differs from the cutting tool 100 according to the first embodiment mainly in that the vibration damping member 8 has a straight shape; however, the other structures are the same as those of the cutting tool 100 according to the first embodiment. The following description will focus on the structures that differ from those of the cutting tool 100 according to the first embodiment.

[0067] Figure 8 This is a top view schematic diagram showing the structure of the cutting tool according to the third embodiment. (As shown) Figure 8 As shown, when viewed in a direction parallel to axis A, each of the multiple vibration damping components 8 has a straight line shape. When viewed in a direction parallel to axis A, each of the multiple vibration damping components 8 extends in a direction intersecting the outer peripheral surface 3. The number of vibration damping components 8 is not particularly limited, for example, it can be eight. Figure 8 As shown, when viewed along axis A, the counterweight component 20 can be a rounded rectangle.

[0068] Figure 9 This is a top view schematic diagram showing the structure of the counterweight component of the cutting tool according to the third embodiment. (As shown) Figure 9 As shown, when viewed in a direction parallel to axis A, the first end face 21 and the second end face 22 are each straight. The first end face 21 is, for example, parallel to the second end face 22. When viewed in a direction parallel to axis A, the through hole 24 can extend perpendicularly relative to the respective directions in which the first end face 21 and the second end face 22 extend.

[0069] (Fourth implementation)

[0070] Next, the structure of the cutting tool 100 according to the fourth embodiment will be described. The cutting tool 100 according to the fourth embodiment is mainly different from the cutting tool 100 according to the first embodiment in the structure in which the cutting insert 7 is installed to the outer peripheral surface 3 of the body portion 10, and is the same as the cutting tool 100 according to the first embodiment with respect to other structures. Hereinafter, the description will be made focusing on the structure different from the cutting tool 100 according to the first embodiment.

[0071] Figure 10 is a schematic plan view showing the structure of the cutting tool according to the fourth embodiment. As shown in Figure 9 the cutting insert 7 can be installed to the outer peripheral surface 3 of the body portion 10. The cutting insert 7 has the longitudinal insert 7a and the transverse insert 7b. The transverse insert 7b is installed to the outer peripheral surface 3 of the body portion 10. The longitudinal insert 7a is installed to the first main surface 1 of the body portion 10. The longitudinal insert 7a is installed to the second main surface 2 of the body portion 10. A plurality of installation recesses 5 can be provided to the inner peripheral surface 4 of the body portion 10. The plurality of installation recesses 5 can each be installed to the plurality of installation protrusions 41 of the adapter 40, respectively.

[0072] Next, the effect of the cutting tool 100 according to the above-described embodiments will be described.

[0073] According to the cutting tool 100 according to the above-described embodiments, the plurality of vibration-proof members 8 are each provided to the body portion 10. The cutting insert 7 is installed to the body portion 10. Therefore, the vibration occurring when the cutting insert 7 contacts the workpiece is each attenuated by the plurality of vibration-proof members 8 provided to the body portion 10. Thus, compared with the cutting tool 100 in which the vibration-proof members 8 are provided to the adapter 40, the vibration during the cutting process can be efficiently attenuated.

[0074] According to the cutting tool 100 according to the above-described embodiments, when viewed in the direction of the axis A, the plurality of vibration-proof members 8 can each be arranged on an imaginary circle B centered on the axis A. Thus, the distance between the axis A and each of the plurality of vibration-proof members 8 is equal, and therefore the vibration during the cutting process can be more efficiently attenuated.

[0075] According to the cutting tool 100 according to the above-described embodiments, when viewed in the direction of the axis A, the plurality of vibration-proof members 8 can each be arranged at equal intervals in the circumferential direction of the imaginary circle B. Thus, the vibration during the cutting process can be equally attenuated in the circumferential direction.

[0076] According to the cutting tool 100 related to the above-described embodiment, the hollow portion 9 surrounded by the inner wall surface 6 can be provided in the main body portion 10. The counterweight member 20 can be disposed in the hollow portion 9 in a state separated from the inner wall surface 6. The counterweight member 20 is separated from the inner wall surface 6, and thus the counterweight member 20 is movable in the hollow portion 9. Thus, the counterweight member 20 vibrates in an anti-phase with respect to the vibration of the main body portion 10. Therefore, the vibration preventing member 8 functions as a dynamic vibration absorber. Thus, the vibration at the time of cutting can be further attenuated compared to the case where the counterweight member 20 and the inner wall surface 6 are in contact.

[0077] According to the cutting tool 100 related to the above-described embodiment, the through-hole 24 can be provided in the counterweight member 20. The plurality of vibration preventing members 8 each can include the pin member 12 that penetrates the through-hole 24 and is attached to the inner wall surface 6, and the elastic member 13 that surrounds the pin member 12 and is in contact with the counterweight member 20 inside the through-hole 24. The counterweight member 20 can attenuate the vibration by the friction between the counterweight member 20 and the elastic member 13 and the friction between the elastic member 13 and the pin member 12. Thus, not only with respect to the radial vibration, but also with respect to the axial and circumferential vibrations, the vibration can be efficiently attenuated.

[0078] According to the cutting tool 100 related to the above-described embodiment, the outer shape of the counterweight member 20 can be a racetrack shape when viewed in the direction of the axis A. Thus, compared to the case where the shape of the counterweight member 20 is linear, the counterweight member 20 can be increased in size. As a result, the vibration at the time of cutting can be further attenuated.

[0079] According to the cutting tool 100 related to the above-described embodiment, the hollow portion 9 surrounded by the inner wall surface 6 can be provided in the main body portion 10. The counterweight member 20 can be disposed in the hollow portion 9 in a state separated from the inner wall surface 6. The through-hole 24 can be provided in the counterweight member 20. The plurality of vibration preventing members 8 each can include the pin member 12 that penetrates the through-hole 24 and is attached to the inner wall surface 6, and the elastic member 13 that surrounds the pin member 12 and is in contact with the counterweight member 20 inside the through-hole 24. The outer shape of the counterweight member 20 can be a racetrack shape when viewed in the direction of the axis A.

[0080] According to the cutting tool 100 according to the above-described embodiment, the counterweight member 20 is separated from the inner wall surface 6, and thus the counterweight member 20 is movable in the hollow portion 9. Thus, the counterweight member 20 vibrates in an opposite phase to the vibration of the main body portion 10. Thus, the vibration prevention member 8 functions as a dynamic vibration absorber. Thus, compared to the case where the counterweight member 20 and the inner wall surface 6 are in contact with each other, the vibration at the time of cutting can be further attenuated. In addition, the counterweight member 20 can attenuate the vibration by the friction between the counterweight member 20 and the elastic member 13 and the friction between the elastic member 13 and the pin member 12. Thus, not only with respect to the radial vibration, but also with respect to the axial and circumferential vibrations, the vibration can be efficiently attenuated. Furthermore, when viewed in the direction of the axis A, in the case where the outer shape of the counterweight member 20 is a racetrack shape, compared to the case where the shape of the counterweight member 20 is a straight line shape, the counterweight member 20 can be increased in size. As a result, the vibration at the time of cutting can be further attenuated.

[0081] Embodiment

[0082] Next, the vibration measurement test will be described. First, a pin end mill according to the sample 1 and the sample 2 was prepared. The pin end mill according to the sample 1 is a comparative example. The pin end mill according to the sample 1 does not have the vibration prevention member 8. The pin end mill according to the sample 2 is an embodiment. The pin end mill according to the sample 2 has the vibration prevention member 8. The pin end mill according to the sample 2 is the cutting tool 100 according to the first embodiment. The thickness T of the main body portion 10 in the axial direction was 17 mm.

[0083] Next, the vibration measurement method will be described. Figure 11 is a side view schematic diagram showing the vibration measurement method. The left cutter 63 is disposed on one side (left side) in the axial direction of the crank shaft 65. The left cutter 63 is attached to the first motor 61. The right cutter 64 is disposed on the other side (right side) in the axial direction of the crank shaft 65. The right cutter 64 is attached to the second motor 62. The vibration measurement sensor 66 is disposed on the first motor 61. The cutting of the crank shaft 65 was performed using the left cutter 63 and the right cutter 64.

[0084] The vibration measurement device was a multi-JOB FET analyzer (model: OR35-10J) manufactured by Toyo Technica Corporation. The number of channels was set to 10 CH. The measurement range was set to 2 kHz. The resolution was set to 2.5 Hz.

[0085] Figure 12 is a graph showing the results of the vibration measurement. The unit g of the vibration is the acceleration of gravity, and is 9.8 m / s 2 . As Figure 12As shown, it was confirmed that the vibration of the pin end mill involved with the sample 2 was smaller than the vibration of the pin end mill involved with the sample 1 in the X (radial) direction and the Y (axial) direction. In the Z (peripheral) direction, the vibration of the pin end mill involved with the sample 2 was substantially the same as the vibration of the pin end mill involved with the sample 1. According to the above results, it was confirmed that the vibration of the pin end mill involved with the sample 2 was mainly able to attenuate the vibration in the X (radial) direction and the Y (axial) direction.

[0086] Figure 13 is a schematic view showing the structure of a thrust surface and a flank surface of a crankshaft. As shown in Figure 13 , the crankshaft 65 has a thrust surface 72 and a flank surface 71. The flank surface 71 is located radially outward of the thrust surface 72. The flank surface 71 and the thrust surface 72 are in different positions in the axial direction.

[0087] After the cutting process of the crankshaft 65 was performed, the surface roughness (Ra: arithmetic average roughness) was measured on the thrust surface 72 and the flank surface 71 of the crankshaft 65. The surface roughness measuring device was a surface roughness measuring device (form: SV-3200L8) manufactured by Mitutoyo Corporation. The measurement length was set to 4.8 mm. The measurement speed was set to 1 mm / sec.

[0088] Figure 14 is a graph showing the results of the surface roughness measurement. As shown in Figure 14 , it was confirmed that the surface roughness (Ra) of the thrust surface 72 in the case where the pin end mill involved with the sample 2 was used was smaller than the surface roughness (Ra) of the thrust surface 72 in the case where the pin end mill involved with the sample 1 was used. Similarly, it was confirmed that the surface roughness of the flank surface 71 in the case where the pin end mill involved with the sample 2 was used was smaller than the surface roughness of the flank surface 71 in the case where the pin end mill involved with the sample 1 was used.

[0089] The chatter phenomenon of the cutting tool 100 occurs due to the repeated contact and non-contact of the cutting edge of the cutting tool 100 and the machined surface of the workpiece (crankshaft 65) in the axial direction. The chatter phenomenon can cause the deterioration of the surface roughness of the machined surface. The attenuation of the vibration in the Y (axial) direction has an effect of suppressing the chatter phenomenon. As a result, it is conceivable that the surface roughness of the machined surface can be reduced.

[0090] It should be considered that the embodiments and examples disclosed herein are illustrative in all aspects and are not restrictive. The scope of the present application is not represented by the above description, but is represented by the claims, and is intended to include all modifications within the meaning and scope equivalent to the claims.

[0091] Explanation of Reference Numerals

[0092] 1 first main surface, 2 second main surface, 3 outer peripheral surface, 4 inner peripheral surface, 5 mounting recess, 6 inner wall surface, 7 cutting insert, 7a longitudinal insert, 7b transverse insert, 8 anti-vibration member, 9 hollow portion, 10 main body portion, 12 pin member, 13 elastic member, 14 positioner, 15 insertion member, 16 fixing member, 20 counterweight member, 21 first end surface, 22 second end surface, 23 third end surface, 24 through hole, 31 first recess, 32 second recess, 40 adapter, 41 mounting protrusion, 42 mounting hole, 50 mounting member, 61 first motor, 62 second motor, 63 left cutter, 64 right cutter, 65 crank shaft, 66 vibration measuring sensor, 71 cheek surface, 72 thrust surface, 100 cutting tool, 200 cutting machining device, A axis, B imaginary circle, C rotation direction, T thickness.

Claims

1. A cutting tool that rotates around an axis, the cutting tool having: a body portion that has an inner peripheral surface and an outer peripheral surface; a cutting insert that is mounted to at least either one of the inner peripheral surface and the outer peripheral surface; and a plurality of vibration-proof members that are provided to the body portion, the plurality of vibration-proof members each include a counterweight member that is made of a material that has a large specific gravity compared to a material that constitutes the body portion, a hollow portion that is surrounded by an inner wall surface is provided to the body portion, the counterweight member is disposed in the hollow portion in a state of being separated from the inner wall surface, a through-hole is provided to the counterweight member, the plurality of vibration-proof members each include: a pin member that penetrates the through-hole and is mounted to the inner wall surface; and an elastic member that surrounds the pin member and is in contact with the counterweight member inside the through-hole, a length direction of the pin member corresponds to a radial direction of the body portion, the elastic member is in contact with an inner surface of the through-hole and the pin member in a circumferential direction of the body portion.

2. The cutting tool according to claim 1, wherein, when viewed in a direction along the axis, the plurality of vibration-proof members are each disposed on an imaginary circle that has the axis as a center.

3. The cutting tool according to claim 2, wherein, when viewed in a direction along the axis, the plurality of vibration-proof members are each disposed at equal intervals in a circumferential direction of the imaginary circle.

4. The cutting tool according to any one of claims 1 to 3, wherein, when viewed in a direction along the axis, an outer shape of the counterweight member is a racetrack shape.

5. A cutting machining device that has: the cutting tool according to any one of claims 1 to 4; and an adapter that holds the body portion.

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