JP3118962U - Tool holder - Google Patents

Abstract

Provided is a tool holder with a blade runout correction function that can easily correct the runout of a cutting tool with a small force, maintain high runout correction accuracy stably, and reduce the tip shape of the holder.
An operation member 333 provided on a ring member 331 fitted on an outer periphery of a cylindrical support portion 313 of a holder body 31 is rotated to rotate a vibration correcting steel ball 334 to a rear end surface 332b of a stop member 332. By adjusting the pressing force, the support portion 313 is configured to be elastically deformed in the radial direction so that the cutting edge runout of the cutting tool 29 approaches zero with the connection base portion 313c with the flange portion 312 as a fulcrum. Further, the holder body 31 can be detachably attached to the chuck member 32 on which the cutting tool 29 is shrink-fitted.
[Selection] Figure 1

Description

  The present invention relates to a tool holder that can correct the runout of a cutting tool mounted on a spindle of a machine tool via a holder, and in particular, a cutting tool such as a small-diameter end mill can be attached to and detached from the holder body via an adapter. The present invention relates to a tool holder with a blade runout correction mechanism that can be inserted.

In order to achieve high-precision machining in machine tool machining, it is necessary to maintain the cutting tool mounting accuracy with high accuracy.
In general, the accuracy when chucking a cutting tool with a tool holder is based on the deflection accuracy of the tip that is a predetermined distance away from the chuck part of the cutting tool in the direction of the cutting edge. Is 3-5 μm. In other words, even if a high-precision chuck is used as a holder for a cutting tool such as a burnishing reamer, a drill, or an end mill, it is difficult to bring the tool blade edge to as close to zero as possible. Therefore, a tool holder capable of correcting the runout of the tool edge has been proposed and put into practical use.

A conventional tool holder with a blade edge correction mechanism will be described with reference to the drawings.
FIG. 1 is a partially cutaway side view showing an example of a conventional tool holder with a blade runout correction mechanism.
In FIG. 1, a tool holder 1 includes a tapered shank portion 2 attached to a main shaft of a machine tool (not shown), a gripping flange 3 formed at the large-diameter side end of the shank portion 2, and the flange. 3, and an arbor 4 provided integrally with the axial end of the anti-shank portion side, and a cutting tool 6 such as a drill is attached to the tip of the arbor 4 by a collet chuck 5.
Further, a step portion 4a having a diameter larger than that of the arbor 4 is formed at a portion where the arbor 4 is connected to the flange 3, and a rotating ring 7 constituting a blade edge correction mechanism is rotatably fitted to the step portion 4a. ing. A fixing bolt 8 is penetrated in a radial direction and screwed to a portion of the rotating ring 7 facing the stepped portion 4a, and the rotating ring 7 is fixed to the stepped portion 4a by the fixing bolt 8. Further, the blade runout correction screws 9 are threaded through the radial direction at four locations in the circumferential direction facing the root portion of the arbor 4 of the rotating ring 7.

  In such a tool holder 1, when correcting the cutting edge runout of the cutting tool 6, the shank portion 2 of the tool holder 1 to which the cutting tool 6 is chucked is mounted on the spindle of the machine tool, and then the cutting tool 6 The test indicator 10 is pressed against the outer peripheral surface of the tip to measure the maximum difference in reading of the test indicator 10 during rotation of the spindle as the blade runout of the cutting tool 6, and from this measured value, the blade runout of the cutting tool 6 is the highest. An angular position is detected. Thereafter, the rotation of the main shaft is stopped and the rotary ring 7 is rotated. One of the blade edge correction screws 9 is aligned with the root portion of the arbor 4 corresponding to the highest angular position of the edge vibration and rotated to this position. The ring 7 is fixed by the fixing bolt 8. After that, by tightening the blade runout correction screw 9 in accordance with the arbor root portion at the angular position where the blade runout is the highest, the arbor 4 is elastically deformed in the tightening direction of the correction screw 9 and the cutting edge of the cutting tool 6 is moved. The misalignment is corrected while looking at the test indicator 10 so that the runout of the blade approaches zero as much as possible. Thereby, the blade runout of the cutting tool 6 can be corrected.

Next, another example of a conventional tool holder with a blade runout correction mechanism will be described with reference to FIG. FIG. 2 is a partially cutaway side view showing another example of a conventional tool holder with a blade edge deflection correcting mechanism.
In FIG. 2, the tool holder 12 includes a tapered shank portion 13 attached to a spindle of a machine tool (not shown), a gripping flange 14 formed at the large-diameter side end of the shank portion 13, The flange 14 has an arbor 15 integrally provided at the end opposite to the shank portion of the flange 14, and a cutting tool 17 such as a drill is attached to the tip of the arbor 15 by a collet chuck 16.

  In FIG. 2, reference numeral 18 denotes a runout corrector for correcting runout of the cutting edge of the cutting tool 17 chucked by the collet chuck 16 on the tool holder 12. And a ring member 181 detachably mounted on the outer periphery of the lock nut 161 of the collet chuck 16, and a push screw 182 screwed into the ring member 181 so as to penetrate the ring member 181 in the radial direction. .

  When correcting the runout of the cutting tool 17 using such a shake corrector 18, first, the shank portion 13 of the tool holder 12 to which the cutting tool 17 is chucked is mounted on the spindle of the machine tool, and the cutting tool The test indicator 19 is pressed against the outer peripheral surface of the tip 17 to measure the maximum difference in reading of the test indicator 19 during rotation of the spindle as the blade runout of the cutting tool 17, and the runout of the cutting tool 17 from the measured value is measured. The highest angular position is detected. After that, the rotation of the main shaft is stopped and the ring member 181 is rotated. The push screw 182 is aligned with the outer peripheral portion of the lock nut 161 corresponding to the angular position where the blade edge swing is the highest, and this outer peripheral portion is aligned with the push screw 182. By applying pressure in the direction of the arrow by tightening, the misalignment of the cutting edge of the cutting tool 17 is corrected while looking at the test indicator 19 so that the fluctuation of the cutting edge approaches zero as much as possible. Thereby, the blade runout of the cutting tool 17 can be corrected. After the shake correction is completed, the shake corrector 18 is removed from the tool holder 12.

However, in the tool holder 1 shown in FIG. 1, the base part of the arbor 4 is pressed from the radial direction of the arbor 4 by the correction screw 9 of the cutting edge correction mechanism provided at the base part of the arbor 4, and the arbor 4 is elastic in the radial direction. Since deformation is to correct the misalignment of the cutting edge of the tool, a large force is required to correct the deflection of the cutting edge. Therefore, there is a problem that such a conventional cutting edge correction method can be applied only to a tool holder for a small diameter cutter.
Moreover, in the tool holder 12 shown in FIG. 2, since the runout corrector 18 is removed from the tool holder 12 after the runout of the cutting edge is corrected, the corrected cutting edge returns to the original runout position. And there is a problem that the vibration correction position of the cutting edge cannot be stably maintained.

  An object of the present invention is to provide a tool holder having a blade runout correction function that can easily correct the runout of a cutting tool with a small force, stably maintain high runout correction accuracy, and reduce the tip shape of the holder. There is.

  The invention of claim 1 is a tool holder capable of correcting the cutting edge runout of a tool, and a shank part for mounting to a main shaft of a machine tool, and a central axis and an axis line of the shank part are aligned with one end of the shank part. And a cylindrical support portion provided on the anti-shank portion side of the flange portion so as to extend in the anti-shank portion side direction with the axis of the flange portion coincident with the axis. A holder body detachably coupled to the support portion, a flange provided at one end of the coupling portion and abutting against a tip surface of the support portion, and the coupling portion on the side opposite to the support portion of the flange A chuck member having a tool mounting arbor portion provided in a predetermined length in the direction opposite to the support portion with the central axis thereof aligned with the axis, and a ring rotatably fitted on the outer periphery of the support portion A member and the phosphorus provided on the support A stop member for holding the member on the support portion, and an eccentric cam portion for correcting the blade edge runout provided in the ring member so as to pass through the ring member in the radial direction so as to be rotatable about the radial axis. An operation member having one end of the operation member and an eccentric cam portion of the operation member, and the other end of the operation member is in contact with a front end surface of the flange portion or an end surface of the ring member. A deflection correction member movably provided in any direction, and the operation member is rotated to move the deflection correction member in a direction pressed against the front end face of the flange portion or the end face of the ring member. The support portion is configured to be elastically deformed in the radial direction so that the cutting edge deflection of the tool approaches zero by adjusting the pressing force.

The invention of claim 2 is characterized in that in the tool holder of claim 1, the deflection correcting member is either a cylindrical pin or a steel ball.
The invention of claim 3 is the tool holder according to claim 1, wherein the ring member includes a balance member for balancing the rotation of the ring member by providing the operation member.
The invention of claim 4 is the tool holder according to claim 1 or 3, wherein the ring member includes a lock screw for fixing the ring member to the support portion.

The invention according to claim 5 is the tool holder according to claim 1, wherein the coupling portion of the chuck member is constituted by a tapered shank whose outer diameter decreases from the flange side toward the anti-flange direction, and the support portion The flange has a tapered hole corresponding to the tapered shank, and after fitting the tapered shank into the tapered hole, a draw bolt provided in the holder body is screwed to the rear end of the tapered shank. The chuck member is configured to be fixed to the holder body by being tightened until it is brought into pressure contact with the front end surface of the support portion.
The invention of claim 6 is the tool holder according to claim 1 or 5, wherein the stop member is screwed by being screwed to a male screw portion formed on the support portion, and the stop member is an outer peripheral surface of the flange. It is also characterized in that it is also screwed to the flange by screwing into the male screw part formed in the above.

  The invention of claim 7 is the tool holder according to claim 1, wherein the coupling portion of the chuck member is constituted by a cylindrical body having an external thread portion on an outer peripheral surface, and the external thread portion of the cylindrical body is screwed into the support portion. The chuck member is fixed to the holder body by screwing the male screw portion of the cylindrical body into the female screw portion and tightening until the flange is pressed against the front end surface of the support portion. It is characterized by comprising.

The invention of claim 8 is the tool holder according to claim 4, wherein the ring member is formed with a female screw hole into which the lock screw is screwed, and the thread of the female screw hole near the outer periphery of the ring member is collapsed. It is processed into a shaped shape.
The invention of claim 9 is the tool holder according to claim 2, wherein the deflection correcting steel ball contacting the front end surface of the flange portion or the rear end surface of the ring member has a flat pressing surface in part. It is characterized by being.
The invention of claim 10 is characterized in that, in the tool holder according to claim 1, 5 or 7, the shank of the cutting tool is chucked on the arbor portion of the chuck member by shrink fitting. .

  According to the tool holder with the blade runout correction mechanism according to the present invention, the operation member of the ring member fitted to the cylindrical support portion of the holder body is rotated to the front end surface of the flange portion or the rear end surface of the ring member. Since the support part is elastically deformed in the radial direction so that the tool tip runout approaches zero by adjusting the pressing force of the runout correction member, the tool tip runout of the cutting tool held by the chuck member can be reduced with a small force. While being able to correct, high runout accuracy can be maintained stably.

Further, according to the present invention, the chuck member for chucking the cutting tool is a two-surface constrained coupling in which the tapered shank is fitted into the tapered hole of the support portion and the lung is pressed against the tip surface of the support portion. Since the structure is adopted, the coupling rigidity between the chuck member and the holder body can be increased.
In addition, according to the present invention, since the stopper member is screwed to the support portion and also to the flange of the chuck member, the pressing force of the shake correcting member when the operation member is rotated is applied to the stopper member. It acts on the chuck member via this, and the elastic deformation of the chuck member in the radial direction becomes easy.
In addition, according to the present invention, since the shank of the cutting tool is chucked to the arbor portion of the chuck member by shrink fitting, the tip shape of the tool holder including the chuck member becomes compact and slim, and the workpiece and Interference can be eliminated.
Further, according to the present invention, since the chuck member is configured to be detachably attached to the holder body, the chuck member chucked with a heavy cutting tool or a finishing tool can be easily attached to the holder body depending on the application. Thus, a single tool holder can be shared.

Hereinafter, a first embodiment of a tool holder according to the present invention will be described with reference to the drawings.
FIG. 3 is a longitudinal side view of the tool holder with a blade runout correcting mechanism in the first embodiment, FIG. 4 is an enlarged sectional view taken along line 4-4 of FIG. 3, and FIG. 5A is the blade tip in the first embodiment. FIG. 5B is an enlarged side view taken along the line BB in FIG. 5A, and a side view showing the cam and the shake correcting steel ball of the shake correcting mechanism in an enlarged manner.
(Embodiment 1)

In FIG. 3, a tool holder 30 that grips a cutting tool 29 such as an end mill includes a hollow holder main body 31, a chuck member 32 that holds the cutting tool 29, a cutting edge deflection correcting mechanism 33 of the cutting tool 29, and the like.
As shown in FIG. 3, the holder main body 31 includes a tapered shank portion 311 that is inserted into the main shaft of a machine tool (not shown), and a gripping flange portion formed at the large-diameter end of the shank portion 311. 312 and a cylindrical shape having a diameter smaller than that of the flange portion 312 provided on the side opposite to the shank portion of the flange portion 312 so as to extend in the direction opposite to the shank portion with the central axis of the shank portion 311 aligned with the axis. And a support portion 313. Further, a tapered hole 314 extending from the tip end surface 313 a to the region of the flange portion 312 is formed concentrically on the shaft center portion of the support portion 313, and the tapered hole 314 extends from the tip end surface 313 a in the support portion 313. It has a tapered shape in which the inner peripheral diameter decreases as it goes to the region of the flange portion 312.

  As shown in FIG. 3, the chuck member 32 includes a tapered shank 321 (corresponding to a coupling portion described in claims) detachably fitted into a tapered hole 314 of the support portion 313, and the tapered member. A flange 322 that is integrally provided at the large-diameter side end of the shank 321 and abuts against the tip end surface 313a of the support portion 313, and the central axis of the tapered shank 321 on the anti-tapered shank side of the flange 322 coincides with the axis and is anti-tapered And a tool mounting arbor portion 323 provided to extend in a predetermined length in the attached shank side direction. Further, a taper hole 324 of a shrink fit (or press fit) having a predetermined depth extending from the tip of the arbor portion 323 toward the flange 322 is formed in the central axis portion of the arbor portion 323. In the hole 324, a taper shank 29a of the cutting tool 29 is chucked by shrink fitting (or press fitting).

  A draw bolt 34 inserted from the rear end side of the holder main body 31 is disposed at the axial center portion in the holder main body 31 and formed at the rear end of the tapered shank 321 fitted in the tapered hole 314. The chuck member 32 can be fixed to the holder main body 31 by screwing the draw bolt 34 into the female threaded portion 321a and tightening the flange 322 until the flange 322 is pressed against the distal end surface 313a of the support portion 313.

The blade edge correction mechanism 33 includes a ring member 331, a stop member 332, an operation member 333 for correcting blade edge vibration, a steel ball 334 for correcting blade edge vibration (corresponding to the vibration correction member described in claims), and the like. ing.
The ring member 331 is fitted to the outer periphery of the support portion 313 so as to be able to rotate in the circumferential direction, and has a rectangular cross section having a thickness corresponding to the outer diameter difference between the flange portion 312 and the support portion 313. ing. Further, as shown in FIGS. 3, 4, and 5 (A), a cylindrical fitting hole 331 a having a desired diameter penetrating in the radial direction of the ring member 331 is formed in a rectangular cross-section portion of the ring member 331. In addition, a guide hole 331b communicating with the fitting hole 331a and penetrating through a rectangular cross section in a direction parallel to the central axis of the support portion 313 is formed. The cutting edge correcting operation member 333 is fitted in the fitting hole 331a so as to be rotatable around the radial axis of the ring member 331, and the steel ball 334 is fitted in the guide hole 331b along the guide hole 331b. It is movably fitted.

  As shown in FIG. 3, the stop member 332 holds the ring member 331 on the support portion 313 and contributes to correction of the blade edge deflection. The stop member 332 is a flange that is in contact with the outer peripheral portion near the tip of the support portion 313 and the tip surface 313 a. A ring shape having an axial length sufficient to cover the outer periphery of 322 is provided. On the inner peripheral surface of the stopper member 332, a male screw portion 313b and a flange 322 formed on the outer peripheral surface near the tip of the support portion 313 are provided. A female screw 332a is formed to be screwed into a male screw portion 322a formed on the outer peripheral surface for screw connection.

  As shown in FIGS. 3, 4, and 5 (A), the operation member 333 has a columnar shape with a diameter corresponding to the fitting hole 331 a, and the operation member 333 is disposed on the outer peripheral surface of the columnar operation member 333. An arcuate cam groove 333a (corresponding to an eccentric cam portion for correcting blade edge deflection described in claims) is formed over the entire circumference, and a steel ball 334 is formed in the cam groove 333a. Are engaged. The cam groove 333 a has an arc surface corresponding to the spherical diameter of the steel ball 334. Further, an operation tool engagement hole 333c is formed on an end surface of the operation member 333 that faces the outer periphery of the ring member 331.

As shown in FIG. 4, the balance for eliminating the unbalance of the rotation of the ring member 331 due to the operation member 333 being provided at the place of the ring member 331 at the opposite position to the place where the operation member 333 is installed. A member 335 is provided in an embedded manner.
Further, as shown in FIG. 4, the ring member 331 is provided with a plurality of lock screws 336 for fixing the ring member 331 to a desired angular position in the circumferential direction with respect to the support portion 313. The lock screw 336 is screwed so as to pass through the rectangular cross-section of the ring member 331 in the radial direction of the ring member 331, and the screw tip of the lock screw 336 engages with the outer peripheral surface of the support portion 313. A groove 313d is formed in a ring shape.
Further, in the female screw hole 331c formed in the ring member 331 for screwing the lock screw 336, the thread 331c1 on the outer peripheral side of the ring member is crushed, and thereby the lock screw screwed into the female screw hole 331c. 336 is prevented from inadvertently falling off the ring member 331. Reference numeral 337 denotes a loosening prevention cushioning material interposed at the tip of the lock screw 336. The lock screw 336 is assembled into the female screw hole 331c from the inside of the ring member 331.

Next, a description will be given of a case where the blade runout of the tool 29 held by the tool holder 30 via the chuck member 32 is corrected using the blade runout correction mechanism 33 configured as described above.
First, after inserting the tapered shank 321 of the chuck member 32 into which the cutting tool 29 is fitted by shrink fitting or press fitting into the tapered hole 314, the draw bolt 34 inserted from the rear end of the holder body 31 is inserted into the tapered shank. The chuck member 32 is attached to the holder main body 31 by being screwed into the female threaded portion 321a of 321 and tightening until the flange 322 is pressed against the distal end surface 313a of the support portion 313. Next, the tool holder 30 holding the cutting tool 29 is mounted on the spindle of the machine tool (not shown). Thereafter, as shown in FIG. 3, the test indicator 28 is pressed against the outer peripheral surface of the tip 29 b of the cutting tool 29, and the maximum difference in reading of the test indicator 28 during the rotation of the spindle is regarded as the blade runout of the cutting tool 29. taking measurement. From this measurement value, the angular position at which the cutting edge runout of the cutting tool 29 is highest is detected.

  Next, the rotation of the spindle of the machine tool is stopped, and the blade edge (blade portion 29b) is moved in the direction indicated by the arrow A1 in FIG. ) Swings as indicated by the phantom line, and the swing is the highest and is shifted to the position indicated by the imaginary line in FIG. 3, first, the ring member 331 is rotated to change the position of the operation member 333 to the angle. After adjusting to the position P1, it is fixed to the support portion 313 by the lock screw 336. In this state, an operation tool (not shown) such as a bar wrench is engaged with the operation tool engagement hole 333c of the operation member 333, and the operation member 333 is rotated. When the operation member 333 is rotated, the shake correcting steel ball 334 is moved toward the rear end surface 332b of the stop member 332 by the cam groove 333a of the operation member 333 according to the rotation amount, and strongly presses the rear end surface 332b. . As a result, the support portion 313 is elastically deformed in the radial direction indicated by the arrow A2 in FIG. 3 with the connection base portion 313c with the flange portion 312 as a fulcrum. That is, by rotating the operation member 333 while looking at the test indicator 28 so that the cutting edge runout of the cutting tool 29 approaches zero as much as possible, the cutting edge of the cutting tool 29 at the misalignment position indicated by the phantom line in FIG. To be at the position indicated by the solid line. As a result, the cutting edge deflection d (μm) of the cutting tool 29 can be corrected to zero.

  According to such a tool holder 30 shown in the first embodiment, the vibration correcting steel is rotated by rotating the operation member 333 provided on the ring member 331 fitted to the outer periphery of the cylindrical support portion 313 of the holder main body 31. By adjusting the pressing force of the ball 334 to the rear end surface 332b of the stop member 332, the support portion 313 is radial so that the runout of the cutting tool 29 approaches zero with the connection base portion 313c with the flange portion 312 as a fulcrum. Therefore, it is possible to correct the runout of the cutting tool 29 with a small force and to maintain high runout accuracy stably.

Further, according to the tool holder 30 shown in the first embodiment, since the stopper member 332 is screw-coupled to the support portion 313 and is also screw-coupled to the flange 322 of the chuck member 32, the operation member 333 is rotated. In this case, the pressing force of the deflection correcting steel balls 334 acts on the chuck member 32 via the stop member 332, and the elastic deformation of the chuck member 32 in the radial direction is facilitated.
Further, according to the tool holder 30 shown in the first embodiment, the chuck member 32 for chucking the cutting tool 29 is fitted with the tapered shank 321 in the tapered hole 314 of the support portion 313 and the flange thereof. Since the two-surface constrained coupling structure in which the 322 is pressed against the distal end surface 313a of the support portion 313 is employed, the coupling rigidity between the chuck member 32 and the holder main body 31 can be increased.

Further, according to the first embodiment, since the shank 29a of the cutting tool 29 is chucked to the arbor portion 323 of the chuck member 32 by shrink fitting, the tip shape of the tool holder 30 including the chuck member 32 is Compact and slim, eliminating interference with the workpiece.
Further, according to the first embodiment, the shrinkage of the cutting tool 29 to the chuck member 32 is expanded by expanding the taper hole 324 by thermal expansion, inserting the taper shank 29a of the cutting tool 29, cooling and chucking. Therefore, the manufacturing cost of the tool holder 30 can be reduced by configuring the holder main body 31 using a normal tool steel and using a material having a large thermal expansion for the chuck member 32.
Further, according to the first embodiment, the chuck member 32 is configured to be detachably attached to the support portion 321 of the holder main body 31 by a pull-in fitting method (or screw connection) using the draw bolt 34. The chuck member 32 chucked with a short heavy cutting tool or a small diameter and long finishing tool can be easily exchanged for the holder main body 31 according to the application, whereby a single tool holder 30 can be shared. .

(Embodiment 2)
Next, a second embodiment of the tool holder according to the present invention will be described with reference to FIGS.
6 is a longitudinal side view of a tool holder with a blade runout correction mechanism according to the second embodiment, FIG. 7 is an enlarged sectional view taken along line 7-7 in FIG. 6, and FIG. 8 is a blade runout correction mechanism according to the second embodiment. It is a side view which expands and shows the cam of this, and a steel ball for shake correction.

In FIG. 6, a tool holder 40 that grips the cutting tool 29 such as an end mill includes a hollow holder main body 41, a chuck member 42 that holds the cutting tool 29, a blade edge correction mechanism 43 of the cutting tool 29, and the like.
As shown in FIG. 6, the holder main body 41 includes a tapered shank portion 411 inserted into the spindle of a machine tool (not shown), and a gripping flange portion formed at the large-diameter side end of the shank portion 411. 412 and a cylindrical shape having a diameter smaller than that of the flange portion 412 provided on the anti-shank portion side of the flange portion 412 so as to extend in the anti-shank portion side direction with the central axis of the shank portion 411 aligned. And a support portion 413. Further, a tapered hole 414 extending from the tip end surface 413a to the flange portion 412 is formed concentrically in the shaft center portion of the support portion 413. The taper hole 414 extends from the tip end surface 413a in the support portion 413. It has a taper shape in which the inner peripheral diameter decreases as it goes to the region of the flange portion 412.

  As shown in FIG. 6, the chuck member 42 is a male screw portion 421 that is detachably screwed and screwed to a female screw portion 414 formed on the inner peripheral wall of the support portion 413 (to the connecting portion described in the claims). And a flange 422 that is integrally provided at one end of the male screw portion 421 and that abuts against the front end surface 413a of the support portion 413, and the axis of the male screw portion 421 coincides with the center axis of the male screw portion 421 on the side opposite to the male screw portion of the flange 422. A tool mounting arbor portion 423 provided extending in a predetermined length in the direction opposite to the male screw portion. Further, a taper hole 424 for shrink fitting or press-fitting with a predetermined depth extending from the tip of the arbor part 423 toward the flange 422 is formed in the central axis part of the arbor part 423. The taper shank 29a of the cutting tool 29 is fitted by shrink fitting or press fitting.

As shown in FIGS. 6 to 8, the blade runout correction mechanism 43 includes a ring member 431, a stop member 432, a blade runout correction operation member 433, and a blade runout correction steel ball 434 (described in the claims). Equivalent to a shake correcting member).
The ring member 431 is fitted to the outer periphery of the support portion 413 so as to be able to rotate in the circumferential direction, and has a rectangular cross section having a thickness corresponding to the difference in outer diameter between the flange portion 412 and the support portion 413. ing. Further, as shown in FIGS. 6 and 7, a cylindrical fitting hole 431a having a desired diameter penetrating in the radial direction of the ring member 431, and the fitting hole 431a are formed in a rectangular cross-section portion of the ring member 431. The guide holes 431b are formed so as to communicate with each other and pass through the rectangular cross section in a direction parallel to the central axis of the support portion 413. The cutting edge correcting operation member 433 is fitted in the fitting hole 431a so as to be rotatable about the radial axis of the ring member 431, and the steel ball 434 is fitted in the guide hole 431b along the guide hole 431b. It is movably fitted.

  As shown in FIG. 6, the stop member 432 holds the ring member 431 on the support portion 413 and contributes to correction of blade edge deflection, and a flange that is in contact with the outer peripheral portion near the front end of the support portion 413 and its front end surface 413 a. It has a ring shape having an axial length sufficient to cover the outer periphery of 422, and a male screw portion 413 b and a flange 422 formed on the outer peripheral surface near the tip of the support portion 413 are formed on the inner peripheral surface of the stopper member 432. A female screw 432a is formed to be screwed into a male screw portion 422a formed on the outer peripheral surface for screw connection.

  As shown in FIGS. 6, 7, and 8, the operation member 433 has a columnar shape with a diameter corresponding to the fitting hole 431 a, and the outer surface of the columnar operation member 433 has a shaft of the operation member 433. An arc-shaped cam groove 433a (corresponding to the eccentric cam portion for correcting blade edge deflection described in the claims) is formed over the entire circumference, and a steel ball 434 is engaged with the cam groove 433a. Is done. The cam groove 433a has an arc surface corresponding to the spherical diameter of the steel ball 434. Further, an operation tool engagement hole 431a is formed on an end surface of the operation member 433 facing the outer periphery of the ring member 431.

As shown in FIG. 7, the balance for eliminating the unbalance of the rotation of the ring member 431 due to the provision of the operation member 433 at the place of the ring member 431 at the position opposite to the place where the operation member 433 is installed. A member 435 is provided in an embedded manner.
Further, as shown in FIG. 7, the ring member 431 is provided with a plurality of lock screws 436 for fixing the ring member 431 at a desired angular position in the circumferential direction with respect to the support portion 413. The lock screw 436 is screwed so as to pass through the rectangular cross-section of the ring member 431 in the radial direction of the ring member 431, and the screw tip of the lock screw 436 engages with the outer peripheral surface of the support portion 413. A groove 413d is formed in a ring shape.
Further, in the female screw hole 431c formed in the ring member 431 for screwing the lock screw 436, the thread 431c1 on the outer peripheral side of the ring member is crushed, and thereby the lock screw screwed into the female screw hole 431c. 436 is prevented from inadvertently falling off the ring member 431. Reference numeral 437 denotes a cushioning material for preventing loosening interposed at the tip of the lock screw 436. The lock screw 436 is assembled into the female screw hole 431c from the inside of the ring member 431.

Next, the case where the blade runout of the tool 29 held by the tool holder 40 via the chuck member 42 is corrected using the blade runout correction mechanism 43 configured as described above will be described.
First, the male screw portion 422a of the chuck member 42 fitted with the cutting tool 29 by shrink fitting or press fitting is screwed into the female screw 432a of the support portion 413, and tightened until the flange 422 is pressed against the tip end surface 413a of the support portion 413. As a result, the chuck member 42 is attached to the holder main body 41. Next, the tool holder 40 holding the cutting tool 29 is mounted on the spindle of the machine tool (not shown). Thereafter, as shown in FIG. 6, the test indicator 28 is pressed against the outer peripheral surface of the blade portion 29 b of the cutting tool 29, and the maximum difference in the reading of the test indicator 28 during the rotation of the spindle is regarded as the blade runout of the cutting tool 29. taking measurement. From this measurement value, the angular position at which the cutting edge runout of the cutting tool 29 is highest is detected.

  Next, the rotation of the spindle of the machine tool is stopped, and the blade edge (blade portion 29b) is moved in the direction indicated by the arrow A1 in FIG. ) Swings as shown by the phantom line, and the swing is the highest and is shifted to the position shown by the phantom line in FIG. 6, first, the ring member 431 is rotated to change the position of the operation member 433 to the angle. After adjusting to the position P1, it is fixed to the support portion 413 by a lock screw 436. In this state, an operation tool (not shown) such as a bar spanner is engaged with the operation tool engagement hole 433c of the operation member 433, and the operation member 433 is rotated. When the operation member 433 is rotated, the deflection correcting steel balls 434 are moved to the rear end surface 432b side of the stop member 432 by the cam groove 433a of the operation member 433 according to the rotation amount, and strongly press the rear end surface 432b. . As a result, the support portion 413 is elastically deformed in the radial direction indicated by the arrow A2 in FIG. 6 with the connection base portion 412a to the flange portion 412 as a fulcrum. That is, by rotating the operation member 433 while looking at the test indicator 28 so that the cutting edge runout of the cutting tool 29 approaches zero as much as possible, the cutting edge of the cutting tool 29 at the misalignment position indicated by the phantom line in FIG. To be at the position indicated by the solid line. As a result, the cutting edge deflection d (μm) of the cutting tool 29 can be corrected to zero.

  According to such a tool holder 40 shown in the second embodiment, the operation member 433 provided on the ring member 431 fitted to the outer periphery of the cylindrical support portion 413 of the holder main body 41 is rotated to correct for shake correction. By adjusting the pressing force of the steel ball 434 to the rear end surface 432b of the stop member 432, the support portion 413 is radial so that the runout of the cutting tool 29 approaches zero with the connection base portion 413a with the flange portion 412 as a fulcrum. Since it is configured to be elastically deformed in the direction, it is possible to correct the runout of the cutting tool 29 with a small force and stably maintain a high runout accuracy. Is obtained.

(Embodiment 3)
Next, a third embodiment, which is a modification of the blade runout correction mechanism 33, will be described with reference to FIG.
FIG. 9 is an enlarged cross-sectional view of a part of a tool holder provided with the blade runout correcting mechanism according to the third embodiment. The same components as those in FIG. The points different from FIG. 3 will be mainly described.
In the blade runout correction mechanism 33 shown in FIG. 9, a flat pressing surface 334 a that is partially cut into a string shape is formed at a location of the runout correction steel ball 334 that is pressed against the rear end surface 332 b of the stop member 332. The flat pressing surface 334 a is brought into surface contact with the rear end surface 332 b of the stop member 332. As a result, the surface pressure between the deflection correcting steel balls 334 and the rear end surface 332b of the stop member 332 can be reduced, and damage to these contact surfaces can be reduced.
(Embodiment 4)

Next, a fourth embodiment, which is a modification of the blade runout correction mechanism 33, will be described with reference to FIG.
FIG. 10 is an enlarged cross-sectional view of a part of a tool holder provided with the blade runout correcting mechanism according to the fourth embodiment. The same components as those in FIG. The points different from FIG. 3 will be mainly described.
In the fourth embodiment shown in FIG. 10, the operation member 333 of the blade runout correction mechanism 33 is rotatably fitted in the fitting hole 331a of the ring member 331, and the ring member 331 has a flange portion from the fitting hole 331a. A guide hole 331c reaching the end surface 312a of 312 is formed in parallel with the central axis of the support portion 313, and a vibration correction steel ball 334 is movably fitted in the guide hole 331c.

In such a blade edge shake correcting mechanism 33, the operating member 333 is rotated to increase or decrease the pressing force to the end surface 312a of the flange portion 312 of the shake correcting steel ball 334, thereby allowing the tool to move in the same manner as shown in FIG. Blade runout can be corrected.
In the tool holder of the modification shown in the fourth embodiment as described above, the same effect as that shown in the first embodiment can be obtained only by changing the deflection correcting pin to a steel ball.
In the fourth embodiment, the portion of the deflection correcting steel ball 334 that is in pressure contact with the end surface 312a of the flange portion 312 may be cut into a flat pressing surface as in the case shown in FIG.
(Embodiment 5)

Next, another embodiment of the blade runout correction mechanism according to the present invention will be described with reference to FIGS.
FIG. 11 is an enlarged cross-sectional view of a part of a tool holder provided with the blade runout correcting mechanism according to the fifth embodiment, and FIG. 12 is an explanatory perspective view showing the operation member and the shake correcting pin in the fifth embodiment in an enlarged manner. In FIG. 3, the same components as those in FIG. 3 are denoted by the same reference numerals, description of the components is omitted, and portions different from those in FIG.

In FIG. 11, reference numeral 50 denotes a blade runout correction mechanism of the cutting tool 29, and the blade runout correction mechanism 50 includes a ring member 501, a stop member 502, an operation member 503 for correcting the blade runout, and a shake correction pin 504. .
The ring member 501 is fitted to the outer periphery of the support portion 313 so as to be able to rotate in the circumferential direction, and has a rectangular cross section having a thickness corresponding to the difference in outer diameter between the flange portion 312 and the support portion 313. ing. Further, as shown in FIG. 11, a cylindrical fitting hole 501a having a desired diameter penetrating in the radial direction of the ring member 501 and a communication hole communicating with the fitting hole 501a are formed in the rectangular cross-section portion of the ring member 501. And the guide hole 501b which penetrates a rectangular cross-section location in the direction parallel to the central axis of the support part 313 is formed, respectively. An operation member 502 for correcting the blade runout is fitted in the fitting hole 501a so as to be rotatable about the radial axis of the ring member 501, and the shake correcting pin 503 moves along the guide hole 501b in the guide hole 501b. It can be fitted.

  As shown in FIG. 11, the stopper member 502 holds the ring member 501 on the support portion 313 and contributes to correction of the blade edge runout. A ring shape having a sufficient length in the axial direction to cover the outer periphery of the support member 322 is provided. On the inner peripheral surface of the stopper member 502, a male screw portion 313b and a flange 322 formed on the outer peripheral surface near the tip of the support portion 313 are provided. A female screw 502a is formed to be screwed into a male screw portion 322a formed on the outer peripheral surface for screw connection.

As shown in FIG. 11 and FIG. 12, the operation member 503 for correcting the blade runout includes a pair of support plates 503a that are rotatably fitted in the fitting holes 501a, and a support plate 503a between the support plates 503a. The cam portion 503b is provided eccentrically from the central axis, and the operation tool engaging hole 503c is formed in one support plate 503a facing the outer periphery of the ring member 501.
One end of the shake correction pin 504 movably fitted in the guide hole 501b is in contact with the cam portion 503b, and the other end is in contact with the rear end surface 502a of the stopper member 502.
Also in the fifth embodiment, the ring member 501 is provided with a balance member as in the case shown in FIG. 4, and the ring member 501 is located at a desired angular position in the circumferential direction with respect to the support portion 313 by a lock screw. It is configured to be fixed to.

Next, the operation of the blade edge shake correcting mechanism 50 configured as described above will be described.
When correcting the blade edge deflection, a tool (not shown) such as a bar wrench is engaged with the operation tool engagement hole 503c of the operation member 503, and the operation member 503 is rotated. When the operation member 503 is rotated, the shake correction pin 504 is moved to the rear end surface 502a side of the stop member 502 according to the rotation amount, and strongly presses the rear end surface 502a. As a result, the support portion 313 is elastically deformed in the radial direction with the connection base portion 313c with the flange portion 312 as a fulcrum. That is, by rotating the operating member 503 so that the cutting edge runout of the cutting tool 29 approaches zero as much as possible, the cutting edge runout d (μm) of the cutting tool 29 shown in FIG. 3 can be corrected to zero.
In the tool holder shown in the fifth embodiment, the same effect as that of the first embodiment can be obtained.

  In the tool holder shown in the fifth embodiment, the shake correction pin 504 may be brought into contact with the front end surface 312a (see FIG. 11) of the flange portion 312 as in the case shown in FIG.

It is a partially cutaway side view showing an example of a conventional tool holder with a blade runout correction mechanism. It is a partial cutaway side view which shows the other example of the conventional tool holder with a blade edge | tip deflection | deviation correction mechanism. It is a vertical side view of the tool holder with a blade runout correction mechanism in Embodiment 1 of the present invention. FIG. 4 is an enlarged cross-sectional view taken along line 4-4 of FIG. (A) is the side view which expands and shows the cam of the blade edge | tip deflection | deviation correction mechanism in this Embodiment 1, and the steel ball | bowl for deflection correction, (B) is an expanded sectional view which follows the BB line of FIG. 5 (A). is there. It is a vertical side view of the tool holder with a blade runout correction mechanism in the second embodiment. It is an expanded sectional view which follows the 7-7 line of FIG. It is a side view which expands and shows the cam and the steel ball for shake correction of the blade edge shake correction mechanism in this Embodiment 2. It is a partial expanded sectional view of the tool holder provided with the blade edge shake correction mechanism concerning Embodiment 3 of this invention. It is a partial expanded sectional view of the tool holder provided with the blade edge deflection | deviation correction mechanism concerning Embodiment 4 of this invention. It is a partial expanded sectional view of the tool holder provided with the blade edge | tip runout correction mechanism concerning Embodiment 5 of this invention. FIG. 10 is an explanatory perspective view showing, in an enlarged manner, an operation member and a shake correction pin in Embodiment 5.

Explanation of symbols

DESCRIPTION OF SYMBOLS 28 Test indicator 29 Cutting tool 29a Shank part 29b Blade part 30 Tool holder 31 Holder main body 311 Shank part 312 Flange part 313 Support part 32 Chuck member 321 Tapered shank 322 Flange 323 Arbor part 33 Cutting edge correction mechanism 331 Ring member 332 Stopping member 333 Operation member 334 Steel ball 34 Draw bolt 40 Tool holder 41 Holder body 411 Shank part 412 Flange part 413 Support part 42 Chuck member 421 Tapered shank 422 Flange 423 Arbor part 43 Cutting edge correction mechanism 431 Ring member 432 Stopping member 433 Stopping member 433 434 Steel ball 50 Cutting edge correction mechanism 501 Ring member 502 Stopping member 503 Operation member 504 Vibration correction pin

Claims (10)

A tool holder capable of correcting the tool edge runout,
A shank portion for mounting on a main shaft of a machine tool, a flange portion provided at one end of the shank portion so as to coincide with the central axis of the shank portion, and a flange portion on the side opposite to the shank portion of the flange portion. A holder body having a cylindrical support portion provided so as to extend in the direction opposite to the shank portion with the central axis aligned with the axis line;
A coupling portion that is detachably coupled to the support portion, a flange that is provided at one end of the coupling portion and that abuts on a front end surface of the support portion, and a central axis and an axis line of the coupling portion on a side opposite to the support portion of the flange A chuck member having a tool mounting arbor portion that is provided at a predetermined length in the direction opposite to the support portion side,
A ring member rotatably fitted to the outer periphery of the support portion;
A stop member provided in the support portion and holding the ring member on the support portion;
An operation member having an eccentric cam portion for correcting a blade runout provided in the ring member so as to pass through the ring member in a radial direction so as to be rotatable about an axis in the radial direction;
The ring member moves in a direction parallel to the center axis of the support portion so that one end abuts on the eccentric cam portion of the operation member and the other end abuts on the front end surface of the flange portion or the rear end surface of the ring member. A vibration correction member provided in a possible manner,
By rotating the operation member and moving the deflection correcting member in a direction pressed against the front end surface of the flange portion or the end surface of the ring member, the support portion is moved by a tool edge by adjusting the pressing force. A tool holder configured to be elastically deformed in a radial direction so as to approach zero.   The tool holder according to claim 1, wherein the deflection correcting member is a cylindrical pin or a steel ball.   The tool holder according to claim 1, wherein the ring member includes a balance member for balancing the rotation of the ring member by providing the operation member.   The tool holder according to claim 1, wherein the ring member includes a lock screw for fixing the ring member to the support portion.   The coupling portion of the chuck member is formed of a tapered shank whose outer diameter decreases as it goes from the flange side to the anti-flange direction, the support portion has a tapered hole corresponding to the tapered shank, and the tapered shank Is inserted into the tapered hole, and a draw bolt provided in the holder body is screwed into the rear end of the tapered shank and tightened until the flange is pressed against the front end surface of the support portion. The tool holder according to claim 1, wherein the member is configured to be fixed to the holder body.   The stopper member is screwed by being screwed to a male screw portion formed on the support portion, and the stopper member is screwed to the flange by being screwed to a male screw portion formed on the outer peripheral surface of the flange. The tool holder according to claim 1 or 5, wherein   The coupling part of the chuck member is constituted by a cylindrical body having an external thread part on an outer peripheral surface, the support part has an internal thread part into which the external thread part of the cylindrical body is screwed, and the external thread part of the cylindrical body is connected to the internal thread part. The tool holder according to claim 1, wherein the chuck member is configured to be fixed to the holder body by being screwed into a portion and tightened until the flange is pressed against the distal end surface of the support portion.   5. A female screw hole into which the lock screw is screwed is formed in the ring member, and a thread near the outer periphery of the ring member in the female screw hole is processed into a crushed shape. Tool holder as described.   The tool holder according to claim 2, wherein the run-out correcting steel ball contacting the front end surface of the flange portion or the rear end surface of the ring member has a flat pressing surface in part.   The tool holder according to claim 1, wherein the shank of the cutting tool is chucked on the arbor portion of the chuck member by shrink fitting.