JP2019072790A - Tool holder - Google Patents

Abstract

To provide a tool holder that can correct a tilt of a blade tip more accurately than before.SOLUTION: A tool holder 10 comprises: a shank member 12 having a central circular hole 16 at a tip part; a tip member 31 having a fitting part 33 at a rear end part; center alignment means that has a plurality of female screw holes 18, formed at a tip large-diameter part 15 of the shank member, whose outer diameter ends are connected to an outer peripheral surfaces of the tip large-diameter part and whose inner diameter ends are connected to the central circular hole and adjustment bolts 64 which are screwed into the female screw holes respectively to contact the fitting part, and adjusts a position in a direction perpendicular to a shaft line O of the tip member, depending on positions into which the adjustment bolts are screwed: and tilt adjustment means 23 that adjusts a posture of the tip member.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a tool holder for chucking a blade, and more particularly to a technique for correcting the tilt of the blade.

  In order to realize high-precision cutting in machine tool processing, it is necessary to maintain the mounting accuracy of the cutting tool with high accuracy. In general, the accuracy when chucking the cutting tool with the tool holder is based on the deflection accuracy of the tip at a predetermined distance away from the chuck portion of the cutting tool in the cutting edge direction, and even if it is a high accuracy tool holder, the deflection accuracy Is 3 to 5 μm. That is, even if a tool such as a burnishing reamer or a drill is chucked by a highly accurate tool holder, it is difficult to make the deflection of the cutting edge of the tool as close to zero as possible. Therefore, conventionally, as described in Japanese Patent No. 3704320 (Patent Document 1) and Japanese Patent No. 4092221 (Patent Document 2), there is known a tool holder which can correct the deflection of the cutting edge of the tool.

  In the tool holder described in the patent document, a ring member is rotatably attached to the outer periphery of the holder body. This ring member incorporates an eccentric cam for edge-slip correction. The eccentric cam is disposed at only one position in the circumferential direction of the tool holder. The eccentric cam is interposed between the roller holding cylinder on the tool holder front end side and the holder main body on the rear end side, and can press the roller holding cylinder to the front end side. The roller holding cylinder is slightly inclined with respect to the axis of the holder main body by being pressed at one place in the circumferential direction by the eccentric cam. As a result, the cutting tool chucked to the roller holding cylinder is also slightly inclined, and the cutting edge (the tip of the cutting tool) is corrected.

  The tool holder described in the patent document is mounted on the spindle of the machining center and rotates with the spindle. That is, the cutting tool or tool chucked to the tool holder described in the patent document is a rotary tool for a machining center. For example, in the case of finishing the work with a rotary tool such as a reamer, it is sufficient to adjust the swing of the cutting edge of the rotary tool to '0'. When the deflection of the cutting edge is set to '0', the deflection of the cutting edge at the entrance of the lower hole of the work becomes '0', and a finished hole is cut and formed in the work along the lower hole.

Patent No. 3704320 Patent No. 4092221 gazette

  The inventor has noticed the problem that even if the rotary holder described in the patent document is interposed between the turret and the tool of the lathe, the workpiece can not be precisely machined. For this reason, in the tool holder described in the patent document, although the roller holding cylinder can be slightly inclined with respect to the axis of the holder main body, the center of the roller holding cylinder is aligned with the axis of the holder main body. I realized that I could not fit it.

  Because, when processing a work with a lathe, the tool attached to the turret of the lathe is not the above-described rotating tool but a stationary tool that does not rotate. For this reason, in the lathe, I realized that it was not enough to correct the inclination of the cutting edge.

  An object of the present invention is, in view of the above-mentioned situation, to provide a tool holder capable of processing a workpiece with higher accuracy than conventional, for a stationary tool for a lathe.

  For this purpose, the tool holder according to the invention is a tool holder attached to the turret of a lathe, which is formed on the holder shank provided at the rear end, the cylinder provided at the tip, the tip of the cylinder A shank member having a large diameter portion extending in the outer diameter direction and a central round hole extending from the large diameter portion toward the rear end, a fitting portion provided at the rear end and fitted in the central circular hole, and the tip And a tip member having tool grasping means for chucking a shank portion of a tool, and a tip end large diameter portion respectively provided at different circumferential positions, the outer diameter end is connected to the outer peripheral surface of the tip large diameter portion A plurality of female screw holes whose inner diameter end is connected to the central round hole, centering means screwed into each of the female screw holes so that the center of the tip member coincides with the center line of lathe spindle, And it is provided on one and a tilt adjusting means for adjusting the attitude of the distal end member.

  According to the present invention, in the tool holder comprising the roller holding cylinder, or the tool holder comprising the taper collet type tool grasping means, or the tool gripping means of another type, the inclination for adjusting the attitude of the tool gripping means The apparatus further comprises adjusting means and centering means for aligning the center of the tip member with the center line of the lathe spindle. The tip member having the tool grasping means is adjusted in both posture and center by these two types of means. According to the present invention, it is possible to adjust the inclination of the cutting tool and the center of the cutting tool to a desired state, and the processing accuracy is improved in the stationary tool.

  The tool holder of the present invention is at least partially made of steel. As a preferred aspect of the present invention, the fitting portion of the tip member is made of steel, and the outer peripheral surface is hardened by quenching. According to this aspect, since the pressing hardness of the outer peripheral surface of the fitting portion is increased, even if the adjustment bolt is repeatedly tightened or loosened to repeatedly contact the outer peripheral surface of the fitting portion, The coefficient of friction of the outer peripheral surface can be maintained low. Therefore, the worker can easily center the center of the tip member on the axis of the shank member.

  With respect to the center line of the lathe spindle, the center line direction position of the centering means is not particularly limited. As a preferred aspect of the present invention, the centering means is disposed on the rear end side of the gauge line of the tool grasping means.

  Although the number and layout of the female screw holes of the centering means are not particularly limited, as a preferable aspect of the present invention, the plurality of female screw holes of the centering means are arranged at equal intervals in the circumferential direction of the tip large diameter portion. According to this aspect, the cutting edge of the stationary tool (cutting tool) can be suitably adjusted. More preferably, female screw holes may be arranged at intervals of 90 ° in the circumferential direction.

  The structure of the tilt adjusting means is not particularly limited. As one aspect, the inclination adjusting means has a stopper member attached and fixed to the outer periphery of the rear end portion of the cylindrical portion, and a cam mechanism disposed between the stopper member and the large diameter end portion. The posture of the tip member is adjusted by pushing the circumferential direction predetermined portion of the diameter portion to the tip side.

  The cam mechanism of the inclination adjusting means may be attached between the stopper member and the large diameter portion by any means, and the structure for attaching the cam mechanism to the stopper member or the shank member is not particularly limited. As one aspect of the present invention, the inclination adjusting means further includes a ring member surrounding the outer periphery of the cylindrical portion, the ring member being interposed between the stopper member and the tip large diameter portion, and the cam mechanism is provided on the ring member . According to this aspect, the cam mechanism can be set to a desired circumferential direction position by rotating the ring member. Therefore, inclination adjustment becomes easy.

  The cam mechanism of the inclination adjusting means may be disposed at one place in the circumferential direction, and the number thereof is not particularly limited. As one aspect of the present invention, the tilt adjusting means has only one cam mechanism. Such one cam mechanism is disposed at any circumferential position of the cylindrical portion. According to this aspect, the posture of the blade can be easily adjusted. In another aspect, the tilt adjusting means includes a plurality of cam mechanisms, and the plurality of cam mechanisms are spaced apart in the circumferential direction of the cylindrical portion. According to another aspect, the posture of the cutting tool can be suitably adjusted using a plurality of cam mechanisms. The plurality of cam mechanisms may be provided on the above-described ring member, and the ring member may be rotatable or may be fixed to the cylindrical portion non-rotatably.

  The structure of the tool grasping means for chucking the cutting tool is not particularly limited. As one aspect of the present invention, the tool grasping means of the tip member includes a tip center hole extending from the tip end of the tip member to the rear end, a female screw formed on the inner periphery of the tip center hole, and a hole bottom of the tip center hole. Taper collet inserted into the tapered hole having a tapered hole extending toward the rear end side from the inside, a tool insertion hole formed on the inner periphery, and a tapered surface formed on the outer periphery, and a subject for engaging with a spanner An annular lock having an engaging portion and an external thread formed on the outer periphery, and the external thread threadingly engages with the internal thread in the tip center hole to push the taper collet into the taper hole to reduce the diameter of the tool insertion hole And a member. According to this aspect, the lock member that pushes the collet chuck into the tapered hole enters the tip center hole of the collet chuck body. Therefore, the projected distance to the tip of the tool chucked by the tool holder as viewed from the tip of the tool holder is shorter than in the prior art. Therefore, it contributes to the improvement of processing accuracy.

  As a preferred aspect of the present invention, the tool grasping means comprises an annular flat pressing surface provided on the lock member and directed to the rear end, and an annular flat receiver provided on the tip of the taper collet and directed to the tip. It further includes an annular plain bearing interposed between the surfaces and surface-treated to reduce friction at both end surfaces. According to this aspect, when the lock member is tightened, the taper collet is pushed so as to follow the axis of the tapered hole by the plain bearing surface-treated to have low friction. The center of the tool can thus be aligned with the axis of the tool holder.

  The shape of the lock member is not particularly limited, but as an aspect of the present invention, the outer diameter of the lock member is equal to the inner diameter of the tip central hole. According to this aspect, the lock member can be accommodated in the tip center hole, and shortening of the tool holder can be achieved.

  The arrangement position of the pressing surface and the plain bearing is not particularly limited, but as a preferred aspect of the present invention, the lock member central hole of the lock member is formed such that the inner diameter of the axially central portion is smaller than the inner diameter of the rear end portion. The pressing surface is provided on the annular step formed by the inner diameter difference of the two, and the plain bearing is accommodated at the rear end portion of the lock member central hole and provided on the inner periphery of the rear end portion of the lock member central hole It further comprises a retaining means for stopping. According to this aspect, when the lock member is separated from the collet chuck body, it is prevented that the plain bearing falls off carelessly.

  The lock member may be any one as long as the taper collet is pushed to the rear end side in the axial direction, but as a preferred aspect of the present invention, the taper collet has an annular nose portion projecting from the annular portion on the inner diameter side with respect to the receiving surface And a ridge protruding outward from the tip of the nose. The lock member is locked between the receiving surface of the taper collet and the heel portion, surrounding the root portion of the nose portion with the lock member central hole. According to this aspect, since the taper collet engages with the lock member, the taper collet is pulled out from the taper hole when the lock member is rotated in the loosening direction, so the work of separating the tool from the tool holder is efficiently performed. be able to.

  The shape of the lock member is not particularly limited, but as one aspect of the present invention, the lock member central hole is formed such that the inner diameter of the axially central portion is smaller than the inner diameter of the tip portion. The collar portion of the taper collet is stored at the tip portion of the lock member central hole. According to this aspect, since the tip end portion of the taper collet is stored in the lock member central hole, it is possible to prevent the tool holder from becoming long.

  The lock member is rotated in the tightening direction or the loosening direction, and thus has an engaged portion for engaging with a spanner or the like. The shape of the engaged portion is not particularly limited, but as a preferred aspect of the present invention, the lock member central hole is formed such that the inner diameter of the tip end portion is smaller than the inner diameter of the rear end portion, and the engaged portion of the lock member is locked A plurality of spaced apart circumferentially spaced members in the circumferential direction of the member and having a bottomed round hole directed to the tip side, and the round hole is an outer diameter side of the tip portion of the lock member central hole and more than the male screw portion of the lock member It is disposed on the inner diameter side. According to this aspect, the engaged portion does not protrude from the lock member to the distal end side, which contributes to downsizing of the lock member.

  The plain bearing reduces the friction between the lock member and the taper collet to facilitate rotation of the lock member so that the taper collet follows the tapered hole of the collet chuck body. The surface treatment of the plain bearing as a preferred aspect of the present invention is a coating treatment or polishing treatment. Coating treatment means forming a low friction layer on the surface of a plain bearing. Polishing refers to the smooth formation of the plain bearing surface itself.

  The collet chuck body is mounted to the machine tool at a holder shank portion at the rear end. The shape of the holder shank portion is not particularly limited. For example, the holder shank is a straight shank extending axially at a predetermined outer diameter.

  As described above, according to the present invention, the position and posture of the cutting tool in the direction perpendicular to the axis can be adjusted by two types of adjustment means. Therefore, the inclination of the cutting edge can be corrected with higher accuracy than in the prior art.

It is a general view showing the tool holder which becomes one embodiment of the present invention. It is a front view showing the embodiment. It is a longitudinal cross-sectional view which expands and shows the front-end | tip part of the embodiment. It is a figure which decomposes | disassembles and shows the embodiment into main components. It is a front view which takes out and shows the lock member of the embodiment. It is a front view which shows the plain bearing of the embodiment. It is an exploded view which shows the plain bearing and locking member of the embodiment. It is an exploded perspective view showing a cam mechanism. It is a sectional view showing a cam mechanism.

  Hereinafter, embodiments of the present invention will be described in detail based on the drawings. FIG. 1 is an overall view showing a tool holder according to an embodiment of the present invention, wherein the left side of the drawing of FIG. 1 is a side view, and the right side of the drawing of FIG. FIG. 2 is a front view showing the tool holder of the embodiment. FIG. 3 is a longitudinal cross-sectional view showing an enlarged tip end of the tool holder of the embodiment. In order to facilitate understanding of the present invention, in FIG. 3, the posture and the position in the direction perpendicular to the axis of the tip member, which are corrected by the centering mechanism and the tilt adjusting mechanism described later, are exaggerated. FIG. 4 is a view showing the tool holder of the embodiment disassembled into main components and includes a side view of the taper collet.

  The tool holder 10 includes a shank member 12 and a tip member 31 as main components. The tip member 31 has tool grasping means for chucking the shank portion 101 of the tool 100. The tool 100 includes, for example, a cutting tool or the like used for cutting, such as an end mill or a drill. In the following description, with respect to the axis O of the shank member 12, the chucking side of the tool 100 (downward in the plane of FIG. 1) is taken as the tip end side in the direction of the axis O (hereinafter simply referred to as the tip end). The rear side (the upper side of the sheet of FIG. 1) is the rear end side in the direction of the axis O (hereinafter simply referred to as the rear end side).

  The shank member 12 and the tip member 31 are connected in series in the direction of the axis O. In principle, the axis of the tip member 31 coincides with the axis O of the shank member 12. However, the center and posture of the tip member 31 are adjusted with respect to the axis O of the shank member 12 by centering means and inclination adjusting means described later.

  With respect to the direction of the axis O, as shown in FIG. 1, the shank member 12 occupies a central region from the rear end of the tool holder 10. The tip member 31 occupies the tip region of the tool holder 10. Although described in detail later, the shank member 12 and the tip member 31 constitute a central hole extending along the axis O so as to penetrate from the front end of the tool holder 10 to the rear end.

  The shank member 12 includes a holder shank portion 13 formed in the rear end region in the direction of the axis O, a cylindrical portion 14 formed in the tip end region, and a tip large diameter portion 15 formed in the tip portion. The holder shank 13 is a straight shank that extends from the rear end of the tool holder 10 to the center at a constant outer diameter. A flat surface 13 p elongated in parallel with the axis O is formed at one circumferential position of the holder shank portion 13. The holder shank portion 13 is mounted on a machine tool (not shown), for example, a tool rest provided on a plurality of rotatable turret heads.

  The front end of the holder shank 13 is coupled to the rear end of the cylindrical portion 14. The cylindrical portion 14 has a bottomed cylindrical shape that is open at the distal end side. The outer diameter of the cylindrical portion 14 is larger than the outer diameter of the holder shank portion 13.

  At the tip of the cylindrical portion 14, a flange-like tip large-diameter portion 15 which spreads to the outer diameter side is formed. A circumferential groove 28 is formed at the boundary between the cylindrical portion 14 and the tip large diameter portion 15. The circumferential groove 28 extends along the outer periphery of the cylindrical portion 14. For this reason, the connection between the cylindrical portion 14 and the large diameter portion 15 at the tip end is made thin, and slight elastic deformation is possible. This is for the inclination adjustment means described later.

  A central round hole 16 extending toward the rear end is formed in the front end surface of the front end large diameter portion 15 which is also the front end surface of the shank member 12. The central round hole 16 has a constant inner diameter centering on the axis O, and constitutes an inner circumferential surface of the tip large diameter portion 15 and the cylindrical portion 14. The tip end member 31 is fitted into the center round hole 16 from the tip end side. A through hole 17 is further formed at the bottom of the central round hole 16. The through hole 17 penetrates the holder shank portion 13 and extends to the rear end of the shank member 12.

  An area from the rear end to the central portion of the tip member 31 constitutes a fitting portion 33. The fitting portion 33 is inserted into the center round hole 16 of the shank member 12 and fitted with the shank member 12. The outer diameter of the fitting portion 33 is formed to be constant in the direction of the axis O corresponding to the inner diameter of the central round hole 16. At an end of the fitting portion 33, a flange portion 34 which is expanded to the outer diameter side is formed. The flange portion 34 of the tip member 31 is not inserted into the central round hole 16 of the shank member 12 and is adjacent to the tip large diameter portion 15 of the shank member 12. The outer diameter of the tip large diameter portion 15 and the outer diameter of the flange portion 34 are the same. The tip large diameter portion 15 and the flange portion 34 are connected in series in the direction of the axis O by a coupling bolt 66 extending in the direction of the axis O, and constitute an outer peripheral surface of the tool holder 10.

  The flange-shaped large-diameter portion 15 which spreads to the outer diameter side about the axis O is slightly elastically deformable. The position in the axial line O direction of the tip large diameter portion 15 usually matches all over the entire circumference of the tip large diameter portion 15, but a portion in the circumferential direction of the tip large diameter portion 15 is more It is also slightly displaceable distally. Then, the flange portion 34 of the distal end member 31 in contact with the distal end surface of the distal end large diameter portion 15 is slightly inclined with respect to the axis O, and the posture of the distal end member 31 changes with the tool 100.

  Here, the connection structure of the shank member 12 and the tip member 31 will be described.

  As shown in FIG. 2, a plurality of recesses 37 are formed in the flange portion 34 of the tip member 31 at intervals in the circumferential direction. Each concave portion 37 is notched to the inner diameter side from the outer peripheral surface of the flange portion 34, and is formed in a step that recedes from the tip end surface of the flange portion 34. In the present embodiment, the concave portions 37 are provided at four locations at equal intervals of 90 ° in the circumferential direction. As shown in FIG. 1, a through hole 38 is provided on the bottom surface of the recess 37 which recedes from the tip end surface of the flange portion 34. Each through hole 38 is connected to the rear end surface of the flange portion 34.

  A plurality of bottomed female screw holes 19 are formed in the tip large diameter portion 15 of the shank member 12 at intervals in the circumferential direction. Each female screw hole 19 extends from the tip end surface of the tip large diameter portion 15 to the rear end side, is disposed to correspond to the circumferential position of each through hole 38, and is connected to each through hole 38. Coupling bolts 66 are passed through the through holes 38 from the tip side. The shaft portion of each connecting bolt 66 is screwed into the female screw hole 19, and the head of each connecting bolt 66 is accommodated in the recess 37 while being locked to the flange portion 34. The tip member 31 is connected and fixed to the shank member 12 by rotating each connecting bolt 66 in the tightening direction.

  A plurality of coupling bolts 66 are circumferentially spaced apart. Specifically, they are arranged at 90 ° intervals. Although the coupling bolts 66 of this embodiment are arranged at equal intervals, the coupling bolts 66 may be arranged at different intervals as a modification not shown.

  Next, the tool grasping means provided on the tip end member 31 will be described.

  An annular tip annular portion 35 projecting to the tip side is formed on the tip surface of the flange portion 34. The inner periphery of the tip annular portion 35 of the tip member 31 defines the tip center hole 36. The tip center hole 36 has a constant inner diameter with respect to the axis O. At the bottom of the tip center hole 36, a tapered hole 32 which is tapered from the tip side toward the rear end is extended. The inner diameter of the tip center hole 36 is larger than the tapered hole 32. The centers of the tapered hole 32 and the tip center hole 36 coincide with the axis of the tip member 31. The tapered collet 41 is inserted into the tapered hole 32 from the tip center hole 36. A lock member 51 is disposed in the tip center hole 36. A female screw portion 36 n is formed on the inner periphery of the distal end annular portion 35. Although described later in detail, the female screw portion 36 n is screwed with the male screw portion 52 formed on the outer periphery of the lock member 51. The bottom of the tip center hole 36 substantially coincides with the gauge line of the tool gripping means for chucking the tool 100. The gauge line is the tip of the axial region where the tapered collet 41 is firmly grasped by the tapered hole 32. With the shank member 12 and the tip member 31 assembled, the through hole 17, the central round hole 16 and the tapered hole 32 are connected in series in this order.

  Referring to FIG. 3 which shows the details of the tool grasping means, the taper collet 41 has a tool insertion hole 49 at its center. The tool insertion hole 49 extends from the front end of the taper collet 41 to the rear end. A tapered surface 42 is formed on the outer periphery of the taper collet 41 so as to increase in diameter from the rear end toward the front end. A flat annular receiving surface 43 directed to the tip side is provided on the tip side of the tapered surface 42.

  The taper collet 41 further has an annular nose portion 44 and a collar portion 45 at the tip. The annular nose portion 44 protrudes from the annular portion on the inner diameter side of the receiving surface 43 toward the distal end. The collar portion 45 protrudes outward from the tip end portion of the nose portion 44.

  The taper collet 41 further has a slot 46, 47. A plurality of slots 46, 47 are arranged at intervals in the circumferential direction. Moreover, the slots 46 and 47 are alternately arranged in the front end area and the rear end area of the taper collet 41, respectively. The slot 46 extends from the front end of the taper collet 41 toward the rear end. For this reason, the tip end portion of the tapered surface 42, the nose portion 44, and the collar portion 45 are discontinuous in the circumferential direction. The slot 47 extends from the rear end of the taper collet 41 toward the front end. Therefore, the rear end side portion of the tapered surface 42 is discontinuous in the circumferential direction. With respect to the axis of the taper collet 41, the axial positions of the splits 46, 47 overlap at the central portion of the taper collet 41.

  The lock member 51 is an annular member, and a male screw portion 52 is formed on the outer periphery. The flat annular tip end surface 53 of the lock member 51 is provided with an engaged portion 54 for engaging with a spanner (not shown). FIG. 5 is a front view showing the lock member 51 of the present embodiment. The engaged portion 54 is a bottomed circular hole spaced apart in the circumferential direction. The engaged portions 54 of the present embodiment are provided at four locations at 90 ° intervals, but the number and layout of the engaged portions 54 are not particularly limited. A spanner (not shown) has a plurality of pin-shaped projections corresponding to the engaged portions 54, and engages with the engaged portions 54 to apply torque in the tightening direction and the loosening direction to the lock member 51. This point will be described in detail later.

  As shown in FIG. 4, the lock member central hole formed at the center of the lock member 51 has a leading end portion 55, a central portion 56 and a rear end portion 57 connected in this order. The inner diameter of tip portion 55 is greater than the inner diameter of central portion 56. For this reason, an annular step 58 is formed at the connection point between the tip portion 55 and the central portion 56. The annular step 58 is an annular surface directed to the tip side. The distal end portion 55 of the lock member central hole is connected to the distal end surface 53 of the lock member 51.

  The axial O direction length of each engaged portion 54, which is a small hole with a bottom, is made equal to or less than the axial O direction length of the tip portion 55 or extends toward the rear end side than the tip portion 55 although not shown. . In the latter case, the axial O direction position of the hole bottom of the engaged portion 54 overlaps the central portion 56. In any case, each engaged portion 54 is disposed more distal than the rear end portion 57.

  The inner diameter of the rear end portion 57 of the lock member central hole is larger than the inner diameter of the front end portion 55. For this reason, an annular step is also formed at the connection point between the rear end portion 57 and the central portion 56. The annular step constitutes an annular flat pressing surface 59 directed to the rear end side. Although described in detail later, the pressing surface 59 applies a pressing force to the taper collet 41.

  A plain bearing 61 is interposed between the pressing surface 59 of the lock member 51 and the receiving surface 43 of the taper collet 41. FIG. 6 is a front view showing the plain bearing 61 of the present embodiment. The plain bearing 61 is an annular disk having a constant thickness, and is formed into a ring plate shape by a hardened and polished steel plate or the like. The end faces of the plain bearing 61, that is, the rear end face and the front end face, are subjected to surface treatment for reducing the frictional resistance with the receiving face 43 and the pressing face 59. Such surface treatment is, for example, ion nitriding treatment, DLC (Diamond Like Carbon) coating treatment, TiN coating treatment, specular lapping treatment, and polishing treatment. Both end faces of the plain bearing 61 may be oil film lubricated in combination with the above-described process or separately.

  The pressing surface 59 of the lock member 51 in surface contact with the end surface of the plain bearing 61 may also be a low-friction flat surface treated to reduce the coefficient of friction, as with the end surfaces of the plain bearing 61. The same applies to the receiving surface 43 in surface contact with the rear end side end face of the plain bearing 61.

  As shown in FIG. 4, the thickness of the plain bearing 61 is smaller than the length of the rear end portion 57 in the direction of the axis O, and the plain bearing 61 is accommodated in the rear end portion 57 of the lock member center hole. The inner peripheral surface of the rear end portion 57 is provided with a slightly protruding projection 57p. The plain bearing 61 is elastically deformable in order to be accommodated in the rear end portion 57. The protrusions 57 p are spaced apart, for example, in the circumferential direction, and engage with the outer edge of the plain bearing 61. The plain bearing 61 is held by the projection 57p so as not to come out of the rear end portion 57 of the lock member central hole, and is held adjacent to the pressing surface 59. Further, as shown in FIG. 7, the plain bearing 61 can be separated from the lock member 51, and can be replaced as appropriate. FIG. 7 is an exploded cross-sectional view of the lock member and the plain bearing.

  Next, centering means for adjusting the position of the tip end member 31 in the direction perpendicular to the axis O will be described.

  As shown in FIG. 3, a female screw hole 18 is formed in the tip large diameter portion 15 of the shank member 12. The female screw hole 18 extends in the radial direction from the outer peripheral surface of the tip large diameter portion 15 to the inner peripheral surface of the center round hole 16 and penetrates the tip large diameter portion 15. As shown by a broken line in FIG. 2, a plurality of female screw holes 18 are formed at intervals in the circumferential direction. In the present embodiment, female screw holes 18 are provided at four locations at equal intervals of 90 ° in the circumferential direction.

  An adjustment bolt 64 is screwed into each female screw hole 18 from the outer diameter side. As shown in FIG. 3, the tip end surface 65 of the adjustment bolt 64 faces the inner diameter side and abuts on the outer peripheral surface of the fitting portion 33 of the tip member 31. In the present embodiment, the tip end member 31 can be moved relative to the shank member 12 in the direction perpendicular to the axis O by appropriately rotating each adjustment bolt 64.

  The outer peripheral surface of the fitting portion 33 is harder than the other portion of the tip member 31. Specifically, HRC (Rockwell hardness) 55 or more, more preferably HRC 60 or more. For example, by hardening the steel tip member 31, the surface portion of the tip member 31 is made harder than the inside. By increasing the pressing hardness of the outer peripheral surface of the fitting portion 33, centering by the adjustment bolt 64 can be facilitated.

  Here, as shown in FIG. 2, each recess 37 is disposed between two female screw holes 18 and 18 adjacent to each other in the circumferential direction. That is, the recesses 37 and the female screw holes 18 are alternately arranged at intervals in the circumferential direction of the flange portion 34. In the present embodiment, the female screw holes 18 and the recesses 37 are arranged at equal intervals in the circumferential direction 45 °.

  The female screw hole 18 as the centering means is disposed on the rear end side of the gauge line (the bottom of the tip center hole 36) of the tool grasping means.

  The procedure for adjusting the position of the tip end member 31 in the direction perpendicular to the axis O using the centering means will be described.

  In the following description, the center of the tip member 31 is understood to mean the center point of the tip member at any position in the axial direction. When the center of the tip member 31 is continuously represented in the axial direction, it is represented by a straight line in FIG. The center X can be slightly displaced relative to the axis O of the shank member 12 by the screwing positions of the plurality of adjusting bolts 64. For example, the adjustment bolt 64 disposed on the left side of the drawing of FIG. 3 is rotated in the tightening direction to be displaced toward the axis O, and the adjustment bolt 64 disposed on the right side of the drawing of FIG. When displaced away from O, the flat tip surface 65 of the adjusting bolt 64 presses the fitting portion 33 to the right in the drawing, and the center X of the tip member 31 is a shank as shown in an exaggerated manner in FIG. It is displaced to the right in the drawing from the axis O of the member 12. As shown in FIG. 2, since the plurality of adjustment bolts 64 are arranged at different circumferential positions, the operator appropriately loosens or tightens the one or more adjustment bolts 64 to allow the tip member 31 to move to the axis O Adjusted in the desired direction at right angles. The displacement amount by the centering means is several [μm] to ten and several [μm].

  Next, inclination adjustment means for adjusting the inclination of the tip member 31 with respect to the axis O will be described.

  As shown in FIG. 3, a ring-shaped stopper member 21 is attached to the outer periphery of the cylindrical portion 14. Specifically, a male screw 14m is formed on the outer periphery of the rear end portion of the cylindrical portion 14, a female screw 21n is formed on the inner periphery of the stopper member 21, and the male screw 14m and the female screw 21n are engaged with each other. The outer diameter of the stopper member 21 is equal to the outer diameter of the tip large diameter portion 15. The stopper member 21 is disposed on the rear end side of the tip large diameter portion 15 with a gap.

  The stopper member 21 is provided with a side lock bolt hole 21s. The side lock bolt holes 21s are female screw holes extending from the outer peripheral surface of the stopper member 21 to the inner peripheral surface. A side lock bolt is screwed into the side lock bolt hole 21s from the outer diameter side of the stopper member 21. The side lock bolt abuts on the outer peripheral surface of the cylindrical portion 14, and the stopper member 21 is attached and fixed to the shank member 12.

  A ring member 22 intervenes between the stopper member 21 and the tip large diameter portion 15. The ring member 22 surrounds the outer periphery of the cylindrical portion 14. By rotating the stopper member 21 in the tightening direction (tip end side), the ring member 22 is pinched between the stopper member 21 and the tip large diameter portion 15 and can not move in the direction of the axis O. Further, the ring member 22 is rotatable in a state where it is not pressed by the stopper member 21 and the tip large diameter portion 15.

  The ring member 22 is provided with a cam mechanism 23. The cam mechanism 23 is disposed along the outer peripheral surface of the cylindrical portion 14. The present embodiment has only one cam mechanism 23.

  By rotating the ring member 22, the circumferential position of the cam mechanism 23 can be changed to any position.

  The cam mechanism 23 of the present embodiment has a cylindrical operation member 24 and a spherical ball 25 and is interposed between the stopper member 21 on the rear end side and the tip large diameter portion 15 on the tip side. The cam mechanism 23 is supported by the tip end surface of the stopper member 21 together with the ring member 22 so that the displacement to the rear end side is suppressed and the pressing force is applied to the tip end side. The cam mechanism 23 presses the ball 25 against the rear end face of the circumferential specific portion of the tip large diameter portion 15 as shown by exaggeration on the left side of the drawing of FIG. Push it out towards the end in the O direction. The circumferential direction specific point is a circumferential position on the opposite side across the axis O as viewed from the direction in which the operator wants the tool 100 to be inclined. The ball 25 is a steel ball or the like.

  FIG. 8 is an exploded perspective view showing the cam mechanism 23. FIG. 9 is a cross-sectional view showing the cam mechanism 23. An eccentric cam groove 24 c is formed on the outer peripheral surface of the operation member 24. The eccentric cam groove 24 c extends in the circumferential direction of the operation member 24. The groove cross section of the eccentric cam groove 24 c has an arc shape corresponding to the outer diameter of the ball 25. However, the groove cross section of the eccentric cam groove 24 c does not have a constant shape over the entire circumference of the operation member 24, but has a groove depth different according to the circumferential position of the operation member 24. The groove width of the eccentric cam groove 24c is the same. Specifically, as shown in FIG. 9, the circle forming the groove bottom of the eccentric cam groove 24 c is eccentric to the outer peripheral circle of the operation member 24.

  The ring member 22 is formed with a circular hole 22 h penetrating in the radial direction, and a small hole 22 j and a hole 22 k extending in parallel with the axis. The small holes 22j extend in the radial direction of the round hole 22h, and connect the inner circumferential surface of the round hole 22h and the tip surface of the ring member 22. The inner diameter of the small hole 22 j corresponds to the outer diameter of the ball 25. The hole 22k is a bottomed hole extending straight from the end face of the ring member 22 and along a tangent line contacting the inner circumferential surface of the round hole 22h.

  In the state where the operation member 24 is inserted into the round hole 22h, one end of the small hole 22j faces the eccentric cam groove 24c. The ball 25 is inserted into the small hole 22 j. The ball 25 is fitted into the eccentric cam groove 24c.

  The hole 22k is adjacent to the outer peripheral surface of the operation member 24 at a position away from the eccentric cam groove 24c. A cylindrical rotation suppressing member 26 made of synthetic resin, hard rubber or the like is inserted into the hole 22k. Further, a holding screw 27 is detachably screwed into the open end of the hole 22k. The holding screw 27 is a plug for closing the hole 22k and prevents the rotation suppressing member 26 from coming off.

  A procedure for adjusting the attitude of the tip member 31 using the inclination adjusting means will be described.

  When a worker inserts a wrench into the wrench engagement hole 24b formed at one end of the operation member 24 and rotates the operation member 24 as shown by the arrow in FIG. 8, the ball 25 is grooved in the eccentric cam groove 24c. According to the small holes 22j. Then, as shown in FIG. 9, when the ball 25 is supported at the shallow location of the eccentric cam groove 24c, the ball 25 is pushed out by the operation member 24 and protrudes from the small hole 22j. On the contrary, when the ball 25 is supported at the deep part of the eccentric cam groove 24c, the ball 25 enters the eccentric cam groove 24c and is accommodated in the small hole 22j.

  One cam mechanism 23 is disposed at any circumferential position and supported by the ring-shaped stopper member 21. By appropriately loosening or tightening the cam mechanism 23 by the operator, the circumferential predetermined portion of the tip large diameter portion 15 is pushed to the tip side more than the remaining portion in the circumferential direction. Then, the attitude of the tip large diameter portion 15 slightly changes with respect to the axis O of the shank member. Then, the posture of the tip member 31 attached and fixed to the tip large diameter portion 15 by the coupling bolt 66 also changes.

  According to the inclination adjusting means of the present embodiment, the attitude of the tip member 31 is adjusted to be inclined in a desired circumferential direction at a desired angle with respect to the axis O. For example, the circumferential predetermined portions of the tip large-diameter portion 15 shown on the left side of the drawing of FIG. 3 are pushed out to the tip side more than the portions different by 180 ° in the circumferential direction shown on the right of the drawing. Thus, as shown in an exaggerated manner in FIG. 3, the tip end member 31 is inclined to the right in the drawing with respect to the axis O of the shank member 12.

  In addition, the rotation suppressing member 26 shown in FIG. 9 is in contact with the outer peripheral surface of the operating member 24 and prevents the operating member 24 from rotating when the operator does not operate it.

  Next, a procedure for chucking a tool such as a cutting tool to the tool holder 10 will be described.

  First, the operator loosens the lock member 51 and rotates it in advance. When the lock member 51 is loosened to such an extent that the lock member 51 protrudes from the distal end surface 35 f of the distal end member 31 to the distal end side, the tool insertion hole 49 of the taper collet 41 is sufficiently expanded in diameter. Next, the operator inserts the shank portion 101 of the tool 100 from the tip end side of the lock member 51 into the tool insertion hole 49 through the lock member central hole and the central hole of the plain bearing 61.

  Next, the operator engages the spanner with the lock member 51 to rotate the lock member 51 in the tightening direction. Then, the lock member 51 is gradually retracted in the axial direction, and the pressing surface 59 of the lock member 51 presses the receiving surface 43 of the taper collet 41 via the plain bearing 61. Then, the taper collet 41 is pushed into the taper hole 32 of the tip member 31, and the slit 46, 47 narrows, so that the diameter of the tool insertion hole 49 is gradually reduced. As a result, the shank portion 101 is tightened on the taper collet 41 all around, and the tool 100 is chucked to the tool holder 10.

  When the lock member 51 pushes the taper collet 41, the plain bearing 61 having a small coefficient of friction is interposed between the two, so the friction between the two is reduced. Therefore, even if the taper collet 41 is not rotated, the lock member 51 can be easily rotated. In addition, relative movement in the direction perpendicular to the axis is possible between the taper collet 41 and the lock member 51. Therefore, even if the lock member 51 is slightly misaligned from the center of the tip member 31 for some reason, the taper collet 41 is pushed along the taper hole 32 and the axis of the taper collet 41 is the center X of the tip member 31. Match Therefore, according to the present embodiment, the tool 100 is chucked so as to coincide with the center X of the tip member 31, and misalignment of the tool 100 is prevented.

  When the tool 100 is separated (unchucked) from the tool holder 10, the reverse procedure to the procedure described above may be performed.

  By the way, the tool holder 10 according to the present embodiment includes the holder shank 13 provided at the rear end, the cylindrical portion 14 provided at the tip, and the tip large diameter portion 15 formed at the tip of the cylinder 14 and expanding in the outer diameter direction. And a shank member 12 having a central round hole 16 extending from the leading end large diameter portion 15 toward the rear end, a fitting portion 33 provided at the rear end and fitted to the central round hole 16, and provided at the front end The tip member 31 having tool grasping means for chucking the shank portion 101 of the tool 100 and the tip end large diameter portion 15 are respectively provided at different circumferential positions, and the outer diameter end is connected to the outer peripheral surface of the tip large diameter portion 15 .., And an adjusting bolt 64 screwed into each of the female screw holes 18 and abutted with the fitting portion 33 of the tip member 31, Multiple adjustments Centering means for adjusting the position of the axis O of the tip member 31 in the right-angled direction according to the screwed-in position of the rut 64, the stopper member 21 attached and fixed to the outer periphery of the rear end of the cylindrical portion 14 Tilt adjusting means for adjusting the attitude of the tip member 31 by pushing a predetermined portion in the circumferential direction of the tip large diameter portion 15 toward the tip side by the cam mechanism 23 having the cam mechanism 23 disposed and supported by the stopper member 21; Equipped with

  According to the present embodiment, in the tool holder 10 including the tool grasping means for chucking the tool 100, the inclination adjusting means for adjusting the attitude of the tool grasping means and the core for adjusting the position of the tool grasping means in the direction perpendicular to the axis O It further comprises a matching means. The tip member having the tool gripping means is adjusted in both the posture and the position perpendicular to the axis by these two types of adjusting means. According to the present invention, the inclination of the cutting tool and the position of the cutting tool in the direction perpendicular to the axis can be adjusted to a desired state, and the processing accuracy when cutting with the cutting tool is significantly improved. The center X of the tip member 31 can be made to coincide with the axis O of the shank member 12 by using these two types of adjustment means for the purpose of centering.

  Further, the fitting portion 33 of the present embodiment is made of steel, and the outer peripheral surface is hardened by the quenching process. Since the outer peripheral surface of the fitting portion 33 is made harder than the other portions of the tip member 31, the coefficient of friction of the outer peripheral surface can be lowered, and the adjusting bolt 64 is repeatedly tightened or loosened and the fitting portion Even when contact with the outer peripheral surface 33 is repeated, the coefficient of friction of the outer peripheral surface of the fitting portion 33 can be maintained low. Therefore, the worker can easily center the center X on the axis O. Further, the tip end member 31 is easily attached to and removed from the center round hole 16 at the tip end of the shank member 12. Further, the tip end member 31 can be smoothly rotated while being fitted in the center round hole 16 of the shank member 12.

  Further, the inclination adjusting means of the present embodiment further includes a ring member 22 surrounding the outer periphery of the cylindrical portion 14, the ring member 22 is interposed between the stopper member 21 and the large diameter portion 15 at the tip, and the cam mechanism 23 is a ring member 22 is provided. As a result, the ring member 22 can be rotated to set the cam mechanism 23 at a desired circumferential direction position, and the inclination direction of the tip member 31 can be adjusted.

  Further, the female screw hole 18 which is a component of the centering means of the present embodiment is disposed on the rear end side relative to the gauge line which substantially coincides with the bottom of the tip center hole 36.

  Further, the female screw holes 18 are arranged at equal intervals in the circumferential direction of the tip large diameter portion 15. This facilitates adjustment in the direction perpendicular to the axis.

  Further, the cam mechanism 23 which is a component of the inclination adjusting means of the present embodiment is disposed at any circumferential position of the cylindrical portion 14. Thereby, the posture of the tip member 31 can be adjusted in the direction desired by the operator, and the adjustment operation becomes easy.

  The cam mechanism 23 is not limited to the present embodiment, and may have a structure shown in FIG. 5 of Japanese Patent No. 4092221 as a modification not shown. Further, as a modification not shown, the inclination adjusting means may have a plurality of cam mechanisms. The plurality of cam mechanisms are circumferentially spaced, specifically, for example, circumferentially equidistantly spaced. As an example, in an annular region between the stopper member 21 and the leading end large diameter portion 15, cam mechanisms 23 are provided at four circumferential positions at intervals of 90 °. According to this modification, the ring member 22 can be eliminated, and by operating one or two cam mechanisms of the plurality of cam mechanisms 23, the attitude of the tip member 31 can be adjusted.

  Further, the tool grasping means of this embodiment includes a tip center hole 36 extending from the tip end of the tip member 31 to the rear end, a female screw portion 36 n formed on the inner periphery of the tip center hole 36, and a hole of the tip center hole 36. A taper collet 41 having a tapered hole 32 extending from the bottom toward the rear end, a tool insertion hole 49 formed on the inner periphery and a tapered surface 42 formed on the outer periphery, and a spanner engaged with the spanner By having the engaged portion 54 for mating and the external thread 52 formed on the outer periphery, the external thread 52 is screwed into the internal thread 36 n in the tip center hole 36 to push the taper collet 41 into the taper hole 32 And an annular lock member 51 for reducing the diameter of the tool insertion hole 49.

  According to the present embodiment, since the lock member 51 is disposed in the tip center hole 36 of the tip member 31, it is compared with, for example, a conventional tool holder having a bag-like lock nut described in Japanese Patent No. 3899324 Thus, the protrusion distance from the tool holder 10 to the tip of the tool 100 can be shortened, and the correction of the inclination of the cutter can be reduced. The axial dimension of the lock member 51 is sufficiently smaller than the axial dimension of the conventional bag-like lock nut. Since the lock member 51 is an outer diameter screw while the conventional bag-shaped lock nut is an inner diameter screw, the axial dimension of the lock member 51 is not more than half the axial dimension of the conventional bag-shaped lock nut. can do.

  The tool grasping means of the present embodiment includes an annular flat pressing surface 59 provided on the lock member 51 and directed to the rear end, and an annular flat provided on the tip of the taper collet 41 and directed to the tip. It further includes an annular plain bearing 61 which is interposed between it and the receiving surface 43 and is surface-treated so that both end surfaces have low friction. By including the plain bearing 61 surface-treated so that at least one end face has low friction, the axis of the tool 100 can be made to coincide with the center X of the tip member 31, and when cutting the work by the tool 100. Machining accuracy is improved.

  Further, in the present embodiment, since the outer diameter size of the lock member 51 is equal to the inner diameter size of the tip center hole, the tip member 31 can accommodate the lock member 51 as shown in FIG. Therefore, the axial length of the lock member 51 completely overlaps the axial length of the tip member 31, and the protrusion distance from the tip surface 35f to the tip of the tool 100 can be made shorter than in the prior art.

  Further, in the present embodiment, in the lock member central hole of the lock member 51, the inner diameter of the central portion 56 in the axial direction is smaller than the inner diameter of the rear end portion 57. The annular step is formed by the difference in inner diameter of the end portion 57. The plain bearing 61 is housed in the rear end portion 57. On the inner periphery of the rear end portion 57 of the lock member central hole, a projection 57p as a retaining means for retaining the plain bearing 61 is further provided.

  Further, the taper collet 41 according to the present embodiment includes an annular nose portion 44 that protrudes from the annular portion on the inner diameter side of the receiving surface 43 toward the tip end, and a flange portion 45 that protrudes from the tip portion of the nose portion 44 to the outer diameter side. Furthermore, it has. That is, the taper collet 41 is constricted at the root portion of the nose portion 44 located between the receiving surface 43 and the collar portion 45. The locking member 51 is engaged with the constricted portion. Specifically, the lock member 51 is locked between the receiving surface 43 of the taper collet 41 and the hook 45 by surrounding the root portion of the nose portion 44 with the lock member central hole. Thereby, when the tool 100 is separated from the tool holder 10, when the lock member 51 is rotated in the loosening direction, the taper collet 41 advances with the lock member 51, and the diameter of the tool insertion hole 49 can be enlarged.

  Further, in the present embodiment, the inner diameter of the central portion 56 in the axial direction of the lock member central hole is smaller than the inner diameter of the tip portion 55, and the flange 45 of the taper collet 41 is the tip portion 55 of the lock member central hole. As a result, the protruding distance from the tool holder 10 to the tip of the tool 100 can be further shortened.

  Further, in the present embodiment, the inner diameter of the front end portion 55 of the lock member central hole is formed smaller than the inner diameter of the rear end portion, and the engaged portions 54 are provided plurally spaced in the circumferential direction of the lock member 51. And the round holes are disposed outside the distal end portion 55 of the lock member central hole and on the inner diameter side with respect to the male screw portion 52 of the lock member 51. Thus, the size of the lock member 51 can be reduced.

  Further, the surface treatment applied to the plain bearing 61 of the present embodiment is a coating treatment or a polishing treatment.

  Further, the holder shank portion 13 of the shank member 12 of the present embodiment is a straight shank extending in the axial direction with a predetermined outer diameter, and the shank member 12 is provided on a tarred head of the NC turret lathe and pivots. Alternatively, it can be mounted on the tool rest of another lathe. Thus, the tool holder 10 can be used as a stationary tool for a lathe.

  Although the embodiments of the present invention have been described above with reference to the drawings, the present invention is not limited to the illustrated embodiments. Various modifications and variations can be made to the illustrated embodiment within the same scope as the present invention or within the equivalent scope.

  The tool holder according to the invention is advantageously used in machine tools.

10 tool holder, 12 shank members,
13 holder shank, 13p flat surface, 14 cylinder,
14m male screw, 15 tip large diameter part, 16 center round hole,
18 female screw holes, 19 female screw holes, 21 stopper members,
21n internal thread, 21s side lock bolt hole,
22 ring members, 22h round holes, 22j small holes,
22k hole, 23 cam mechanism, 24 operation members,
24b wrench engagement hole, 24c eccentric cam groove, 25 ball,
26 rotation restraint member, 27 holding screw, 28 circumferential groove,
31 tip member, 32 taper hole, 33 fitting part,
34 flanges, 35 tip annulus, 53 tip face,
36 tip center hole, 36n internal thread, 37 recess,
41 taper collet, 42 taper surface, 43 receiving surface,
44 nose, 45 butt 49 tool insertion holes,
51 lock member, 52 male screw portion, 54 engaged portion,
55 front end, 56 center, 57 rear end,
57p projection, 58 annular step, 59 pressing surface,
61 plain bearings, 64 adjustment bolts,
66 joint bolt, 100 tool, 101 shank part,
O Axis of the shank, center of the X tip.

Claims (14)

A tool holder attached to the lathe turret,
A holder shank portion provided at the rear end portion, a cylindrical portion provided at the front end portion, a front end large diameter portion formed at the front end portion of the cylindrical portion and expanding in the outer diameter direction, and extending from the front end large diameter portion to the rear end side A shank member having a central round hole;
A fitting member provided at the rear end and fitted to the central round hole, and a tip member provided at the tip and having tool grasping means for chucking the shank of the tool;
The plurality of female screw holes respectively provided at different circumferential positions of the large diameter portion at the distal end, the outer diameter end is connected to the outer peripheral surface of the large diameter portion at the distal end, and the inner diameter end is connected to the central round hole; Centering means for adjusting the center of the tip member to the center line of the lathe spindle according to screwing positions of a plurality of the adjusting bolts, having an adjusting bolt screwed into each and abutting against the fitting portion of the tip member; ,
A tool holder comprising: tilt adjusting means provided on at least one of the shank member and the tip member to adjust the attitude of the tip member.   The tool holder according to claim 1, wherein the fitting portion is made of steel and the outer circumferential surface is hardened by quenching.   The tool holder according to claim 1, wherein the centering means is disposed on a rear end side of a gauge line of the tool grasping means.   The tool holder according to any one of claims 1 to 3, wherein the plurality of female screw holes of the centering means are arranged at equal intervals in the circumferential direction of the large diameter portion at the tip.   The inclination adjusting means has a stopper member attached and fixed to the outer periphery of the rear end portion of the cylindrical portion, and a cam mechanism disposed between the stopper member and the large diameter portion at the tip end. The tool holder according to any one of claims 1 to 4, wherein the posture of the tip member is adjusted by pushing a circumferential predetermined portion of the tip large diameter portion toward the tip side. The tilt adjusting means further includes a ring member surrounding the outer periphery of the cylindrical portion,
The ring member is interposed between the stopper member and the tip large diameter portion.
The tool holder according to claim 5, wherein the cam mechanism is provided on the ring member. The tilt adjusting means has one or more of the cam mechanisms,
The tool holder according to claim 5, wherein the cam mechanism is disposed at any circumferential position of the cylindrical portion. The tool grasping means is
A tip center hole extending from the tip end of the tip member to the rear end side;
A female screw formed on the inner periphery of the tip center hole;
A tapered hole extending from the bottom of the tip central hole toward the rear end side;
A tool insertion hole formed on the inner periphery, and a taper collet having a tapered surface formed on the outer periphery and inserted into the tapered hole;
It has an engaged portion for engaging with a spanner, and an external thread formed on the outer periphery, and the external thread is screwed to the internal thread in the tip center hole to make the taper collet into the tapered hole. The tool holder according to any one of claims 1 to 7, further comprising: an annular lock member that reduces the diameter of the tool insertion hole by pushing.   The tool grasping means includes an annular flat pressing surface provided on the lock member and directed to the rear end, and an annular flat receiving surface provided on the distal end of the taper collet and directed to the distal end. 9. The tool holder according to claim 8, further comprising an annular plain bearing interposed between and having a surface treated to reduce friction at both end faces. The lock member central hole of the lock member is formed such that the inner diameter of the axially central portion is smaller than the inner diameter of the rear end portion, and the pressing surface is provided on the annular step constituted by the inner diameter difference
The plain bearing is housed at the rear end portion,
The tool holder according to claim 9, further comprising a retaining means provided on an inner periphery of the rear end portion of the locking member central hole for retaining the plain bearing. The taper collet further includes an annular nose portion projecting to the tip side from an annular portion on the inner diameter side of the receiving surface, and a collar portion projecting to the outer diameter side from the tip portion of the nose portion
The tool holder according to claim 10, wherein the lock member is locked between the receiving surface of the taper collet and the hook portion by surrounding the root portion of the nose portion with the lock member central hole. . The lock member central hole is formed such that the inner diameter of the axially central portion is smaller than the inner diameter of the tip portion,
The tool holder according to claim 11, wherein the flange portion of the taper collet is accommodated at the tip end portion of the lock member central hole. The lock member central hole is formed such that the inner diameter of the tip end portion is smaller than the inner diameter of the rear end portion,
The to-be-engaged portion is a bottomed circular hole provided in a plurality at intervals in the circumferential direction of the lock member and directed to the tip side,
13. The tool holder according to claim 12, wherein the round hole is disposed outside the tip end portion of the lock member center hole and further inside the exit than the male screw portion of the lock member.   The tool holder according to any one of claims 9 to 13, wherein the surface treatment is a coating treatment or a polishing treatment.

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