JP2023008312A - indexing tool holder - Google Patents

Abstract

To provide an indexing tool holder capable of converting linear motion of a polishing tool into a rotation step operation, and automatizing rotation of a prescribed angle of the polishing tool by being attached to an NC machine tool.SOLUTION: An indexing tool holder comprises: drive means in which a linear drive part is stored in an indexing tool holder body, and reciprocating and moving linearly the linear drive part; a linear motion groove in which, there is provided a guide groove on a facing surface of the linear drive part facing the indexing tool holder body, to which a protrusion member is engaged, the protrusion member energized toward the linear drive part from the indexing tool holder body, in which the guide groove has a depth which has a longitudinal direction parallel to the linear direction and which is varied according to the position of an indexing rotation angle; and an inclination groove which has a longitudinal direction in a direction crossing the linear direction, and whose depth is varied, among indexing rotation angles. The linear groove and inclination groove are alternately arranged along a circumferential direction of the linear drive part, and are continuously arranged so as to circulate on the facing surface of the linear drive part in the circumferential direction.SELECTED DRAWING: Figure 2

Description

The present invention relates to an indexing tool holder that utilizes a groove mechanism for converting linear motion into rotary step motion (hereinafter referred to as indexing motion).

BACKGROUND ART When machine tools such as lathes and cylindrical grinders are used in the cutting of metals, resins, etc., burrs protruding outward are found on the edges of products after machining. The presence of such burrs may hinder post-processes and assembly of parts, and may affect the functions of the product, so they must be removed.

The occurrence of burrs due to cutting is caused by the plastic deformation that occurs on the machined surface, leaving the portion that protrudes outside the edge uncut. The size and location of occurrence are different. For this reason, as a method for removing burrs, it has hitherto been performed to rotate the processed product and manually polish it using a polishing brush, a whetstone, sandpaper, or the like.

However, such manual polishing needs to be performed on each workpiece one by one, which requires labor and time.

In order to ensure safety, recent machine tools are equipped with an interlock that prevents the operation of the lathe while the safety door is open. It is In a machine tool equipped with such an interlock device, it is difficult to rotate the work spindle while the safety door is open and perform manual polishing.

Japanese Patent Application Laid-Open No. 2021-49610

For the above reasons, instead of manual polishing, a polishing tool such as a polishing brush or whetstone is attached as one of the processing tools of the NC machine tool, and the polishing tool is moved by the NC program to perform polishing. I can think of a way. However, in general machine tools such as NC lathes, the workpiece is rotated and a machining tool such as a cutting tool that moves in a straight line or a curve is pressed against the workpiece for machining. I can't. When polishing is performed by attaching a cylindrical polishing tool to such an NC machine tool, only a portion of the cylindrical side surface of the polishing tool comes into contact with the workpiece, making it difficult to use the entire circumference of the cylindrical side surface. be. Moreover, if it is desired to change the point of action of the polishing tool on the workpiece, it is necessary to temporarily stop the machining by the machine tool, manually change the rotation angle of the polishing tool, and fix it again. A method using a rotating rotary tool is also conceivable.

Therefore, the present invention has been made in view of the above-mentioned matters, and converts the linear motion of a polishing tool into a rotary step motion, and attaches it to an NC machine tool, thereby automating the rotation of the polishing tool through a predetermined angle. An object of the present invention is to provide an indexing tool holder capable of

The present invention has been made to achieve the above objects, and is characterized by the following.

An indexing tool holder according to the present invention is an indexing tool holder capable of converting the motion of a rectilinear driving part driven in an axial direction into a rotational motion of a constant angle to change the position of a tool action point, a driving means for accommodating the linear driving portion in an indexing tool holder main body and linearly reciprocating the linear driving portion; and a projection biased from the indexing tool holder body toward the linear driving portion A guide groove with which a member engages is formed in a surface of the rectilinear driving portion facing the indexing tool holder body, and the guide groove has a longitudinal direction parallel to the rectilinear motion direction at the position of the indexing rotation angle. It has a linear motion groove whose depth changes and an inclined groove whose longitudinal direction intersects with the linear motion direction between the index rotation angles, wherein the linear motion groove and the inclined groove , alternately arranged along the circumferential direction of the linear driving portion, and arranged continuously so as to circulate in the circumferential direction on the facing surface of the linear driving portion.

In the indexing tool holder according to the present invention, the linear motion groove and the inclined groove each have a base portion having the largest groove depth and a tip portion having a groove depth gradually decreasing along the longitudinal direction from the base portion. and is suitable.

In the indexing tool holder according to the present invention, the tip portion of one of the linear motion grooves and the inclined grooves is arranged continuously with the base portion of the other of the adjacent inclined grooves and the linear motion grooves. preferably provided.

In the indexing tool holder according to the present invention, it is preferable that there are two or more positions in the linear motion direction of the base with which the projecting member is engaged in the reference state.

In the indexing tool holder according to the present invention, it is preferable that the rectilinear driving section includes a collet as tool fixing means and a cap for tightening the collet, and is formed with an inner diameter tapered surface for receiving the collet.

In the indexing tool holder according to the invention of the present application, it is preferable that the indexing tool holder body is provided with a return-acting elastic body that biases the rectilinear driving portion in the rectilinear direction.

In the indexing tool holder according to the present invention, it is preferable that the drive means advances the rectilinear drive portion by fluid pressure.

In the indexing tool holder according to the present invention, it is preferable that the drive means advances the linear drive portion by mechanical movement of a linear motion unit mounted on the machine tool.

In the indexing tool holder according to the present invention, the driving means causes the linear driving section to abut on a fixed protrusion provided on the machine tool by the movement of the turret type tool rest according to the NC program, thereby moving the linear driving section. It is preferable to move forward.

In the indexing tool holder according to the present invention, it is preferable that the drive means advances and reverses the rectilinear drive portion by fluid pressure.

In the indexing tool holder according to the present invention, the fluid pressure is preferably coolant pressure used in machine tools.

Preferably, in the indexing tool holder according to the present invention, the attached tool is a grinding tool.

The above summary of the invention does not list all of the features necessary for the invention, and subcombinations of these feature groups can also be inventions.

According to the indexing tool holder of the present invention, it is possible to change the linear motion of the polishing tool to the rotary step motion with a simple structure. Also, by attaching it to an NC machine tool, it is possible to automate the rotation step operation of the polishing tool in a low-cost manner and change the point of action of the polishing tool on the workpiece.

BRIEF DESCRIPTION OF THE DRAWINGS The perspective view which shows an example of the NC machine tool to which the indexing tool holder which concerns on embodiment of this invention is attached. FIG. 4 is a cross-sectional view of the indexing tool holder according to the first embodiment of the present invention, where (a) is a partial cross-sectional view showing the standard state, (b) is a partial cross-sectional view showing the advanced state, and (c) is a sectional view taken along the line AA of FIG. 2(a); 3(a) is a front view of a rectilinear drive member having groove arrangement A according to the present invention, (b) is an enlarged cross-sectional view taken along line BB of FIG. 3(a), and (c) is a view of FIG. CC enlarged sectional view. 4(a) is a front view of a rectilinear drive member having groove arrangement form B of the present invention, (b) is an enlarged cross-sectional view taken along line DD of FIG. 4(a), and (c) is a view of FIG. EE enlarged sectional view. (a) is a front view of a rectilinear driving member having groove arrangement form C of the present invention, (b) is an enlarged cross-sectional view taken along line FF of FIG. 5(a), and (c) is a view of FIG. GG enlarged sectional view. FIG. 4 is a cross-sectional view showing an example of the drive means of the linear drive unit using coolant pressure according to the first embodiment of the present invention; FIG. 5 is a cross-sectional view showing a modification of the drive means of the linear drive unit using coolant pressure according to the first embodiment of the present invention; FIG. 4 is a cross-sectional view showing an example of the drive means of the linear drive section using mechanical motion according to the first embodiment of the present invention; FIG. 5 is a cross-sectional view showing a state where an indexing tool holder according to a second embodiment of the present invention is attached to a turret tool holder;

Preferred embodiments for carrying out the present invention will be described below with reference to the drawings. In addition, the following embodiments do not limit the invention according to each claim, and not all combinations of features described in the embodiments are essential for the solution of the invention. .

FIG. 1 is a perspective view showing an example of an NC machine tool to which an indexing tool holder according to the embodiment of the invention is attached, and FIG. 2 is a cross section of the indexing tool holder according to the first embodiment of the invention. 2A is a partial cross-sectional view showing a reference state, FIG. 2B is a partial cross-sectional view showing an advanced state, and FIG. In this specification, the terms "front-rear direction" and "linear motion direction" are defined as directions indicated by arrows in FIG. In this specification, the term "indexing" refers to positioning and rotating by a predetermined angle stepwise around the axis. Further, the term "coolant pressure" as used herein means the pressure of the cutting fluid used for machining.

[Usage example of indexing tool holder]
The indexing tool holder according to the present invention holds a polishing tool or the like, and is attached via a turret tool holder 101 to a turret type tool rest 100 provided in a machine tool such as an NC lathe, as shown in FIG. be done.

The NC lathe shown in FIG. 1 includes a headstock 200 that rotates a work at a position facing a turret-type tool post 100, and a chuck 201 that fixes the work is attached to the tip of the headstock 200. In such an NC lathe, the main motion for cutting or polishing is the rotation of the headstock 200 to which the workpiece is attached, and the straight or curved line of the turret-type tool post 100 to which the indexing tool holder and cutting tools according to the present invention are attached. The motion is used as a feed motion, and it is mainly used to cut out cylindrical products. In this embodiment, the case where the indexing tool holder is attached to the NC lathe having the turret type tool post 100 has been described, but the machine tool using the indexing tool holder is not limited to this, Other machine tools such as comb blade turrets may also be used.

[First embodiment]
[Component configuration of the indexing tool holder]
As shown in FIG. 2, the indexing tool holder 1 according to the present embodiment accommodates a rectilinear drive unit 10 for gripping a deburring tool 41, which is a polishing tool, and the rectilinear drive unit 10 so as to be slidable in the front-rear direction. An indexing tool holder body 30 is provided. In addition, a spring cap 36 is provided in front of the indexing tool holder main body 30 , and a return elastic body 35 for biasing the rectilinear driving portion 10 in the front-rear direction is provided. is provided with a stopper portion 50 for urging the rectilinear driving portion 10 perpendicularly to the front-rear direction.

The rectilinear drive unit 10 includes a substantially cylindrical rectilinear drive member 11 , a collet 42 for holding a deburring tool 41 , and a collet nut 43 for fixing the collet 42 .

The rectilinear driving member 11 includes a cylindrical sliding portion 12 having a cylindrical side surface slidable against the inner diameter surface of the indexing tool holder body 30 , and a cylindrical sliding portion 12 positioned in front of the cylindrical sliding portion 12 . It has a substantially cylindrical shaft portion 15 formed coaxially with respect to the axis.

As shown in FIG. 2(a), the cylindrical sliding portion 12 has a predetermined clearance from the inner diameter surface of the indexing tool holder main body 30 so that the rectilinear driving portion 10 can properly slide under coolant pressure, which will be described later. It has a cylindrical side that forms a Moreover, it is preferable that the cylindrical side surface of the cylindrical sliding portion 12 is finished with a smooth surface so that it can slide smoothly with respect to the indexing tool holder main body 30 . In order to prevent coolant from leaking due to the clearance between the indexing tool holder body 30 and the cylindrical sliding portion 12, a circumferential groove is provided at the rear end of the cylindrical side surface of the cylindrical sliding portion 12, and an O-ring or the like is provided. It is also possible to install a sealing material of

In addition, as shown in FIG. 3A, the cylindrical side surface of the cylindrical sliding portion 12 is provided with a plurality of linear motion grooves 21 having a longitudinal direction parallel to the axial direction of the cylindrical sliding portion 12 and intersecting with the axial direction. A plurality of slanted grooves 22 having longitudinal directions are formed. The linear motion grooves 21 and the inclined grooves 22 are engaged with spherical bodies 51, which will be described later, and function as guide grooves when the linear driving portion 10 performs linear motion and indexing operations. In the present embodiment, there are a plurality of arrangements of these grooves, and the linear movement and indexing operations of the linear drive unit 10 differ depending on the arrangement of the grooves. The arrangement of the grooves and the operation of the rectilinear drive unit 10 in this embodiment will be described later in detail.

A shaft portion 15 having a cylindrical side surface smaller than the outer diameter of the cylindrical side surface of the cylindrical sliding portion 12 extends from the front end surface of the cylindrical sliding portion 12 . A spring support surface 16 for supporting the bearing surface of the return-acting elastic body 35 is formed between the cylindrical side surfaces of .

The cylindrical side surface of the shaft portion 15 is formed to have an outer diameter smaller than the inner diameter of the return-acting elastic body 35 and penetrates the inner-diameter side of the return-acting elastic body 35 . The outer diameter of the shaft portion 15 is preferably formed so as to secure an appropriate clearance with the inner diameter of the return-acting elastic body 35 so as not to rub against the return-acting elastic body 35 . Further, in order to prevent contact between the return-acting elastic body 35 and the shaft portion 15, the outer diameter of the shaft portion 15 on the side of the spring support surface 16 may be increased and a stepped guide may be provided.

A deep hole capable of accommodating the collet 42 is formed in the shaft portion 15 , and an inner diameter tapered surface 17 capable of fitting with the side surface of the collet 42 is provided near the entrance of the deep hole. A threaded portion 18 for tightening the collet nut 43 is formed at the tip of the shaft portion 15 . In order to suppress the rotation of the rectilinear drive member 11 when the collet nut 43 is tightened, it is preferable that the parallel two planes 19 that can be gripped with a tool such as a wrench are formed behind the threaded portion 18 .

According to the shaft portion 15 formed in this way, for example, as shown in FIG. 2A, by tightening the collet nut 43 attached to the screw portion 18, radial slits are formed in the longitudinal direction. The alternate side surfaces of the collet 42 are pressed against the inner diameter tapered surface 17 , and the inner diameter surface of the collet 42 is reduced substantially parallel to allow the deburring tool 41 to be gripped. The method of holding the deburring tool 41 is not limited to the structure of the inner diameter tapered surface 17 and the collet 42, and any known fixing method can be used.

As shown in FIG. 2(a), the indexing tool holder main body 30 has a predetermined clearance between the cylindrical side surface of the cylindrical sliding portion 12 and the linear driving portion 10 so that the linear driving portion 10 can properly slide under coolant pressure, which will be described later. has an inner diameter surface that defines a Moreover, it is preferable that the inner diameter surface of the indexing tool holder main body 30 is finished to have a smooth surface so that the rectilinear drive unit 10 can slide smoothly.

The indexing tool holder body 30 has a cylindrical side surface that is inserted into the inner diameter of the turret tool holder 101, and a circumferential groove is formed at the rear end of the cylindrical side surface to prevent leakage of coolant, which will be described later. O-rings are installed. The rear edge of the indexing tool holder main body 30 is preferably chamfered or the like to prevent the O-ring from being damaged and to facilitate attachment.

Further, on the cylindrical side surface of the indexing tool holder main body 30, when the indexing tool holder 1 is attached to the turret tool holder 101, a holding surface 31 that serves as a fixing mechanism for restraining movements in the rotational direction and the front-rear direction. , and a through hole 32 for attaching the stopper portion 50 .

As an example is shown in FIG. 6, the pressing surface 31 is a flat surface formed on the outer diameter surface of the indexing tool holder body 30 and is formed at a position corresponding to the set screw 103 attached to the turret tool holder 101. be. The indexing tool holder 1 is attached to the turret tool holder 101 by tightening the setscrew 103 so that it is restrained from moving in the rotational direction and in the forward and backward directions. In this embodiment, the pressing surface 31 is a continuous plane corresponding to the positions of the two setscrews 103 arranged side by side in the axial direction of the indexing tool holder 1. The position and arrangement are not limited to this, and it may be divided into a plurality of parts according to the position of at least one set screw 103 . Further, as a mechanism for fixing the indexing tool holder 1 to the turret tool holder 101, known means such as a key may be used.

As shown in FIGS. 2A and 2C, the through-hole 32 is a through-hole formed in a direction perpendicular to the axial direction of the indexing tool holder body 30. A side surface of the through hole 32 located on the inner diameter side is formed so as to receive a sphere 51 described later. A threaded portion for screwing is formed.

The return-acting elastic body 35 passes through the shaft portion 15 and is accommodated in the inner diameter of the indexing tool holder main body 30, and a compression coil spring is preferably used. One bearing surface of the return-acting elastic body 35 is supported by the spring support surface 16 of the rectilinear driving member 11, and the other bearing surface is supported by a spring cap 36, which will be described later. It is mounted under a biased condition.

The spring cap 36 is attached to the front end surface of the indexing tool holder main body 30 by a fastening member such as a bolt, with the shaft portion 15 penetrating through the center. The mounting method of the spring cap 36 is not limited to using bolts or the like, and other mounting methods may be used as long as the mounting method is capable of resisting the spring load of the return-acting elastic body 35 . For example, the spring cap 36 and the indexing tool holder body 30 may be threaded to form a pair, or may be attached by a known attachment means such as a mechanical connection such as caulking. Alternatively, the indexing tool holder body 30 may be formed integrally with the spring cap 36 .

The stopper portion 50 is attached to the through hole 32 of the indexing tool holder body 30 and is composed of a sphere 51 , an elastic body 52 for the sphere, and a set screw 53 .

The sphere 51 is in contact with the bottom surface of the linear motion groove 21 or the inclined groove 22, the sphere elastic body 52 is positioned between the sphere 51 and the set screw 53, and the set screw 53 is screwed into the threaded portion of the through hole 32. , supports one bearing surface of the elastic body 52 for a sphere. At this time, the spherical elastic body 52 is biased by a predetermined load, and the spherical body 51 presses the bottom surface of the linear motion groove 21 or the inclined groove 22 . Moreover, the entire length of the set screw 53 is formed to such a length that the head thereof does not protrude from the outer diameter of the indexing tool holder main body 30 when attached to the through hole 32 . In the present embodiment, the case where the sphere 51 is spherical has been described, but the shape of the sphere 51 is not limited to this, and may be any projecting member having a smoothly rounded tip. Cannonball-shaped pins, etc. are also acceptable.

[Arrangement form of linear motion grooves and inclined grooves, and linear motion/indexing operation of linear drive part]
Next, the arrangement of the linear grooves and the inclined grooves provided in the cylindrical sliding portion 12 of the linear drive member 11 and the linear movement and indexing operation of the linear drive portion 10 in each arrangement will be described in detail.

FIG. 3(a) is a front view of a rectilinear drive member having a groove arrangement form A of the present invention, and FIG. 4(a) is a front view of a rectilinear drive member having a groove arrangement form B of the present invention. FIG. 5(a) is a front view of a rectilinear driving member having the groove arrangement form C of the present invention.

[Groove Arrangement Form A]
As shown in FIG. 3A, the arrangement A of the grooves in this embodiment includes a plurality of linear motion grooves 21 having a longitudinal direction parallel to the axial direction of the cylindrical sliding portion 12 and a direction crossing the axial direction. It is composed of a plurality of inclined grooves 22 having a longitudinal direction at . The groove bottom surfaces of the linear motion groove 21 and the inclined groove 22 are arcuate in the cross section orthogonal to the longitudinal direction of the groove.

As shown in FIG. 3(b), the linear groove 21 has a base portion 21a with the deepest groove depth on the front side of the cylindrical sliding portion 12, and along the longitudinal direction of the linear groove 21 from the base portion 21a. , and has a tip portion 21b whose groove depth gradually becomes shallower. The base portions 21a of the plurality of linear motion grooves 21 are arranged at equal angles along the circumferential direction of the cylindrical sliding portion 12, for example.

As shown in FIG. 3(c), the inclined groove 22 has a base portion 22a with the deepest groove depth on the rear side of the cylindrical sliding portion 12, and gradually expands along the longitudinal direction of the inclined groove 22 from the base portion 22a. has a tip portion 22b with a shallow groove depth. The base portions 22a of the plurality of inclined grooves 22 are arranged at equal angles along the circumferential direction of the cylindrical sliding portion 12, for example. Moreover, it is preferable that the depth of the inclined groove 22 varies along the circular arc of the cylindrical side surface of the cylindrical sliding portion 12 at right angles.

As shown in FIG. 3A, the linear groove 21 and the inclined groove 22 are arranged so that the base 22a of the inclined groove 22 is positioned on the longitudinal axis of the linear groove 21. 21 is connected to the inclined groove 22 . Also, the base portion 21 a of the adjacent linear motion groove 21 is positioned on the longitudinal axis of the inclined groove 22 , and the inclined groove 22 is connected to the adjacent linear motion groove 21 . The linear motion grooves 21 and the inclined grooves 22 maintain the positional relationship described above and are repeatedly arranged along the circumferential direction of the cylindrical sliding portion 12 . Therefore, on the cylindrical side surface of the cylindrical sliding portion 12, the linear motion grooves 21 and the inclined grooves 22 are alternately continuous to form a circulation groove that goes around in the circumferential direction.

According to the arrangement of the linear motion grooves 21 and the inclined grooves 22 as described above, as shown in FIG. As shown in FIG. 3(c), since the base portion 21a with a deep groove is connected to the tip portion 21b with a shallow groove depth, the connecting portion between the linear motion groove 21 and the inclined groove 22 has a gentle bottom surface. and a steep bottom surface are formed. It is preferable that the edges of the steps 23 are smoothly connected.

Next, the linear movement and indexing operation of the rectilinear drive unit 10 having the groove arrangement form A as described above will be described.

FIG. 2(a) shows a state in which the rectilinear drive unit 10 does not receive an external load (hereinafter referred to as a "reference state"). In the reference state, the rectilinear drive unit 10 is urged rearward in the rectilinear motion direction by the elastic body 35 for rectilinear motion, and is stationary due to the engagement of the ball 51 with the base portion 21 a of the rectilinear groove 21 . .

When a load is applied from the rear by a driving means, which will be described later, the rectilinear drive unit 10 in the standard state slides on the inner diameter of the indexing tool holder body 30, bends the return-motion elastic body 35, and advances. At this time, the rectilinear driving portion 10 rectilinearly moves by being guided by the linear motion groove 21 by the ball 51, and the pressing position of the ball 51 is along the linear motion groove 21 from the base portion 21a shown in FIG. 3(b). It moves to the tip portion 21b. When the rectilinear drive unit 10 further advances, the pressing position of the spherical body 51 overcomes the step 23 and shifts to the base portion 22 a of the inclined groove 22 . At this time, as shown in FIG. 2(b), the sphere 51 engages with the base portion 22a, and the rectilinear driving portion 10 stops advancing. (Hereinafter, the state at this time will be referred to as the "advance state".)

When the load applied by the drive means is removed from the linear drive unit 10 in the forward state, the repulsive force of the urged elastic body 35 pushes the linear drive unit 10 back from the front. moves backwards. At this time, the rectilinear drive unit 10 is guided by the slant groove 22 on the sphere 51 and moves backward while rotating about the axis, and the pressure contact position of the sphere 51 is the base 22a shown in FIG. 3(c). , along the inclined groove 22 to the front end portion 22b.

As described above, the inclined groove 22 is formed so that the groove depth gradually decreases from the base portion 22a to the tip portion 22b. , is formed steeply. Therefore, when the rectilinear drive unit 10 moves rearward, the pressing position of the ball 51 positioned on the base 22a does not climb over the step 23 and return to the rectilinear groove 21, and the inclined groove 22 is reliably selected.

After that, when the rectilinear drive unit 10 is further pushed back, the pressing position of the ball 51 moves over the step 23 and moves to the base 21a of the rectilinear groove 21 connected to the inclined groove 22, and the rectilinear drive unit 10 moves backward. Stop. At this time, the base portion 21a with which the ball 51 engages is the base portion 21a of the linear groove 21 adjacent to the linear groove 21 engaged in the reference state. is rotated by an angle of

In this way, the rectilinear drive unit 10 can be indexed by linearly reciprocating the rectilinear drive unit 10 by the driving means and the return elastic member 35 . Further, since the linear groove 21 and the inclined groove 22 are continuous circulation grooves so as to make one round in the circumferential direction, the linear driving unit 10 is repetitively linearly reciprocated to continue the indexing of the linear driving unit 10. can be done.

Further, according to the arrangement A of the grooves, when the rectilinear drive unit 10 moves forward, only the linear motion is performed without performing the indexing motion. Therefore, the necessary load of the drive means on the linear driving portion 10 is sufficient as long as it can compress the return-acting elastic body 35, and should be made smaller than the case where the return-acting elastic body 35 is compressed while performing the indexing operation. can be done. Further, when a compression coil spring is used for the return-acting elastic body 35, the compression coil spring is expanded to perform the indexing action. Therefore, there is no possibility that the torsional force of the compression coil spring acting against the direction of indexing rotation acts.

Further, by making the angle of the longitudinal direction of the inclined groove 22 intersect the axial direction of the cylindrical sliding portion 12 in the opposite direction, the direction of indexing rotation of the rectilinear drive portion 10 can be reversed.

[Groove Arrangement Form B]

As shown in FIG. 4( a ), the groove arrangement B described below has an angle in the longitudinal direction of the inclined grooves and a difference between the linear motion groove and the base of the inclined grooves in comparison with the groove arrangement A described above. Different position.

That is, as shown in FIG. 3A, the inclined groove 22 of the groove arrangement form A has a base portion 22a located behind the cylindrical sliding portion 12 and intersects the axial direction from the base portion 22a forward. While the groove depth gradually decreases in the direction, the inclined groove 22' of the groove arrangement form B has the base portion 22a' located in front of the cylindrical sliding portion 12 as shown in FIG. 4(a). , the groove depth is formed gradually shallower in the direction crossing the axial direction toward the rear from the base portion 22a'.

Further, in the linear motion groove 21 of the groove arrangement form A, the base portion 21a is located in front of the cylindrical sliding portion 12, and the groove depth gradually becomes shallower toward the rear in the axial direction. In the direct-acting groove 21' of form B, the base portion 21a' is located behind the cylindrical sliding portion 12, and the groove depth is formed gradually shallower toward the front in the axial direction.

In addition, the bottom shape of the groove, the connecting portion between the linear groove and the inclined groove, etc. are formed by the same configuration as in the groove arrangement form A, and the same reference numerals are used for these configurations. , and detailed description thereof will be omitted.

Next, the linear movement and indexing operation of the linear drive unit 10 having the groove arrangement form B as described above will be described.

When the rectilinear drive unit 10 is in the reference state, the rectilinear drive unit 10 is urged rearward in the rectilinear motion direction by the return motion elastic body 35, and the ball 51 engages with the base 22a' of the inclined groove 22'. It stands still.

When a load is applied from the rear by a driving means, which will be described later, the rectilinear drive unit 10 in the standard state slides on the inner diameter of the indexing tool holder body 30, bends the return-motion elastic body 35, and advances. At this time, the rectilinear driving portion 10 moves forward while rotating around the axis by being guided by the slant groove 22' by the sphere 51, and the pressing position of the sphere 51 changes from the base portion 22a' to the slant groove 22'. to the tip 22b'. When the linear driving portion 10 further advances, the pressure contact position of the ball 51 overcomes the step 23 and shifts to the base portion 21a' of the linear groove 21', and the linear driving portion 10 stops advancing and enters an advancing state.

When the load applied by the drive means is removed from the linear drive unit 10 in the forward state, the repulsive force of the urged elastic body 35 pushes the linear drive unit 10 back from the front. moves backwards. At this time, the rectilinear drive unit 10 rectilinearly moves rearward by being guided by the rectilinear groove 21' by the spherical body 51, and the pressure contact position of the spherical body 51 changes from the base 21a' along the rectilinear groove 21' to the distal end. 21b'. When the linear drive unit 10 is further pushed back, the pressing position of the ball 51 moves over the step 23 and moves to the base portion 22a' of the inclined groove 22' adjacent to the base portion engaged in the reference state, and the linear drive unit 10 stops reverse.

In this way, the indexing operation of the linear drive unit 10 by the arrangement form A of the grooves is performed when the linear drive unit 10 is pushed back by the repulsive force of the return-acting elastic body 35 and moves backward. , the indexing operation of the rectilinear drive unit 10 according to the groove arrangement form B is different in that the rectilinear drive unit 10 is indexed when pushed forward by the drive means.

[Groove Arrangement Form C]
As shown in FIG. 5(a), in the groove arrangement form C described below, in contrast to the groove arrangement form A described above, the positions of the bases of the adjacent linear motion grooves are alternately arranged in the cylindrical sliding portion. 12 are arranged one behind the other in the axial direction.

The base portion 24a of the linear motion groove 24 of the groove arrangement form C is formed with a distance L behind the base portion 21a of the adjacent linear motion groove 21 in the axial direction. The grooves 24 are alternately arranged along the circumferential direction of the cylindrical sliding portion 12 .

The base 24a of the linear motion groove 24 is positioned on the longitudinal axis of the inclined groove 25, and the base 21a of the linear motion groove 21 is positioned on the longitudinal axis of the inclined groove 22. Circulation grooves are formed on the cylindrical side surface of the cylindrical sliding portion 12 so that the grooves 21 , the inclined grooves 25 , the linear motion grooves 24 , and the inclined grooves 22 are repeatedly and continuously connected in this order. Since the bases 22a and 25a of the inclined grooves 22 and 25 are arranged along the circumferential direction of the cylindrical sliding portion 12, the longitudinal direction of the inclined grooves 22 and 25 is parallel to the axial direction of the cylindrical sliding portion 12. intersect at different angles.

In addition, the bottom shape of the groove, the connecting portion between the linear groove and the inclined groove, etc. are formed by the same configuration as in the groove arrangement form A, and the same reference numerals are used for these configurations. detailed description is omitted.

Next, the linear movement and indexing operation of the rectilinear drive unit 10 having the groove arrangement form C as described above will be described.

As in the case of having the groove arrangement form A, the rectilinear driving part 10 having the groove arrangement form C is pushed out by the driving means from the reference state to reach the forward state, and is moved from the forward state by the repulsive force of the return-action elastic body 35. Indexing occurs as it is pushed back and moves backwards.

In the groove arrangement form C, the adjacent bases 21a and 24a are arranged at positions spaced apart by the distance L in the axial direction of the rectilinear driving unit 10, as described above. Therefore, for example, when the sphere 51 is engaged with the base portion 21a in the initial reference state, the sphere 51 engages with the base portion 24a when the rectilinear driving portion 10 makes one reciprocation by linearly moving and indexing. The rectilinear drive unit 10 completes its operation when it is advanced by the distance L in the axial direction with respect to the reference state.

That is, each time the linear drive unit 10 linearly reciprocates in the axial direction, the stop position in the axial direction is changed back and forth for indexing. In the present embodiment, the base portion 21a and the base portion 24a are separated by the distance L in the axial direction, and the linear drive unit 10 has two stop positions. The position of is not limited to this, and for example, the stop positions of the rectilinear drive unit 10 may be formed so as to be spaced apart by three or more stages.

[Driving Means of Straight Drive Unit]
Next, the driving means of the linear driving section 10 in this embodiment will be described. In the present embodiment, the drive means applies a load to the rear of the linear drive unit 10 using the coolant pressure used in the NC machine tool, and a method to apply the load to the rear of the linear drive unit 10 by mechanical operation. It is divided into

[Driving Means Using Coolant Pressure]
FIG. 6 shows an embodiment of the drive means of the linear drive section 10 using coolant pressure. In this drive means, the indexing tool holder 1 is attached to a turret tool holder 101 for oil hole tools.

A turret tool holder 101 corresponding to an oil hole tool has a lid member 102 airtightly attached to the rear thereof, forming a closed space 105 between the indexing tool holder 1 and the lid member 102 . Further, behind the turret tool holder 101, a coolant discharge port 104 is provided that communicates with the sealed space 105 via a passage provided in the lid member 102. By discharging the coolant of the NC machine tool, The pressure within the enclosed space 105 can be increased.

The space between the indexing tool holder 1 and the turret tool holder 101 is sealed by an O-ring attached to the rear end of the indexing tool holder body 30. A clearance between the sliding portion 12 and the cylindrical side surface is set so that the rectilinear driving portion 10 can appropriately slide under coolant pressure. Therefore, due to the increase in pressure in the closed space 105, surface pressure is applied to the rear end surface of the rectilinear driving portion 10, and the rectilinear driving portion 10 is pushed forward. As for the rearward driving of the rectilinear drive unit 10, when the coolant is stopped, as described above, the rectilinear drive unit 10 can pushed back.

Further, the configuration of the turret tool holder used for the driving means using coolant pressure is not limited to the above. As shown in FIG. 107 may be airtightly attached. The coolant inlet 108 is provided with a connection structure such as a pipe taper screw, so that it can be connected to a pipe or the like to which coolant is supplied. Between the indexing tool holder 1 and the lid member 107, a closed space 109 similar to that described above is formed. By using such a turret tool holder 106 , the coolant may directly flow into the closed space 109 to increase the pressure and drive the rectilinear driving section 10 .

In the present embodiment, a load due to coolant pressure is applied to the rear end surface of the linear driving portion 10, and the linear driving portion 10 is linearly reciprocated by arranging the return elastic body 35 in front of the linear driving portion 10. Although the method has been described, the direction in which the load is applied is not limited to this. The drive unit 10 may be linearly reciprocated.

[Driving Means Using Mechanical Action]
FIG. 8 shows an embodiment of the driving means of the rectilinear drive 10 using mechanical action. In this drive means, the indexing tool holder 1 is attached to a turret tool holder 110 which is open at the rear.

A linear motion unit such as a cylinder is attached to the NC machine tool in which this drive means is used, and the piston rod tip 111 of the linear motion unit contacts the rear end face of the linear drive portion 10. there is In order to drive the rectilinear drive unit 10, the rectilinear drive unit 10 is operated to push in the piston rod tip 111, thereby moving the rectilinear drive unit 10 forward. As for the rearward driving of the rectilinear driving portion 10, the rectilinear driving portion 10 is pushed back by the repulsive force of the return elastic body 35 acting on the front end portion of the cylindrical sliding portion 12, as described above.

In addition, by utilizing the movement of the turret type tool post 100 by the NC program, the rear end surface of the linear drive unit 10 is brought into contact with a fixed protrusion or the like installed on the machine tool, and the linear drive unit 10 is advanced. I don't mind.

[Second embodiment]
In the indexing tool holder 1 according to the first embodiment described above, the rectilinear driving portion 10 is advanced by the driving means and moved backward by the repulsive force of the elastic body 35 for reciprocating motion, thereby performing the linear motion and indexing motion. I explained the output tool holder. An indexing tool holder 6 according to a second embodiment described below is linearly moved in the front-rear direction by a method different from that of the first embodiment to perform an indexing operation. The same or similar configurations as those of the above-described first embodiment are denoted by the same reference numerals, and detailed descriptions thereof are omitted.

[Component configuration of the indexing tool holder]
FIG. 9 is a cross-sectional view showing a state in which an indexing tool holder element according to a second embodiment of the present invention is attached to a turret tool holder.

The indexing tool holder 6 according to the second embodiment, as shown in FIG. 9, is composed of a rectilinear drive section 60 that grips the turning tool 44 and a sleeve 80 that slidably accommodates the rectilinear drive section 60. . A cylindrical side surface of the sleeve 80 is provided with a stopper portion 50 for urging the rectilinear driving portion 60 perpendicularly to the front-rear direction.

As shown in FIG. 9 , the rectilinear drive unit 60 includes a substantially cylindrical rectilinear drive member 61 , a collet 42 for holding a turning tool 44 , and a collet nut 43 for fixing the collet 42 .

The rectilinear drive member 61 includes a cylindrical sliding portion 62 having a cylindrical side surface slidable against the inner diameter surface of the sleeve 80 , and a cylindrical sliding portion 62 located in front of the cylindrical sliding portion 62 and slidable relative to the axis of the cylindrical sliding portion 12 . It has a shaft portion 15 formed coaxially.

The cylindrical sliding portion 62 is slidable on the inner diameter surface of the sleeve 80 and has circumferential grooves for mounting O-rings on both ends in the axial direction so as to prevent leakage of coolant, which will be described later. The cylindrical side surface of the cylindrical sliding portion 62 is preferably finished with a smooth surface so that it can slide smoothly on the sleeve 80 .

In the cylindrical side surface of the cylindrical sliding portion 62, as in the first embodiment, a plurality of linear motion grooves 21 having a longitudinal direction parallel to the axial direction of the cylindrical sliding portion 62 and a A plurality of oblique grooves 22 having a longitudinal direction are formed. Since the arrangement of the grooves and the operation of the rectilinear drive unit 60 performed in the second embodiment are the same as in the first embodiment, detailed description thereof will be omitted.

The sleeve 80 slidably accommodates the rectilinear driving portion 60 and has an inner diameter surface corresponding to the O-rings attached to both ends of the cylindrical sliding portion 62 so as to prevent leakage of coolant, which will be described later. The inner diameter surface of the sleeve 80 is preferably finished to have a smooth surface so that the rectilinear driving portion 60 can slide smoothly. Also, the overall length of the sleeve 80 is formed longer than the overall length of the cylindrical sliding portion 62 . Therefore, as shown in FIG. 9, when the indexing tool holder 6 is attached to a turret tool holder 112 described later and in the standard state, the front end surface of the cylindrical sliding portion 62 and the front lid member 113 described later can be aligned. A closed space 115 is formed between. The entire length of the sealed space 115 is formed on the cylindrical side surface of the cylindrical sliding portion 62 so that the front end surface of the cylindrical sliding portion 62 and the rear end surface of the front cover member 113 are in contact with each other when the rectilinear driving portion 60 moves forward. are formed corresponding to the linear motion grooves 21 and the inclined grooves 22 . Therefore, when the rectilinear driving portion 60 performs the linear motion/indexing operation, the front end surface of the cylindrical sliding portion 62 and the rear end surface of the front lid member 113 come into contact with each other, thereby stopping the forward movement of the rectilinear driving portion 60 . , to the forward state.

The cylindrical side surface of the sleeve 80 has a pressing hole bottom surface 81 that serves as a fixing mechanism when the indexing tool holder 6 is attached to the turret tool holder 112 and a through hole 32 for attaching the stopper portion 50 .

Also, the cylindrical side surface of the sleeve 80 is formed so as to fit properly with the inner diameter surface of the turret tool holder 112 so as to prevent coolant leakage. The assembling of the sleeve 80 to the turret tool holder 112 is not limited to the fitting shown in FIG. 9, and a sealing material such as an O-ring may be used. In such cases, a circumferential groove is formed in the cylindrical side surface of the sleeve 80 or the inner diameter surface of the turret tool holder 112 .

The indexing tool holder 6 of the second embodiment constructed as described above is attached to a turret tool holder 112 having a front cover member 113 and a rear cover member 114 in front and rear in the axial direction as shown in FIG. .

The front lid member 113 is formed with a through hole 116 through which the shaft portion 15 passes, and is airtightly attached to the front end surface of the turret tool holder 112 by fastening means (not shown).

A circumferential groove is provided on the inner diameter surface of the through hole 116 , and an O-ring is attached between the through hole 116 and the shaft portion 15 to prevent leakage of coolant.

A predetermined gap 117 is formed between the rear end face of the front lid member 113 and the front end face of the sleeve 80 when the indexing tool holder 6 is mounted. A groove portion 120 is formed in the rear end face of the front lid member 113 at a position corresponding to a coolant inlet hole 118 to be described later, and connects the inner diameter of the coolant inlet hole 118 and the sleeve 80 . In addition, in order to apply surface pressure to the front end surface of the cylindrical sliding portion 62 by a high-pressure coolant, which will be described later, the rear end surface of the front cover member 113 has an inner diameter smaller than the outer diameter of the cylindrical sliding portion 62 and a groove portion. A counterbore communicating with 120 is preferably formed.

A set screw 103 is attached to the turret tool holder 112 to constrain the movement of the indexing tool holder 6 in the rotational direction and the longitudinal direction. Further, the turret tool holder 112 is provided with a coolant inlet hole 118 having a pipe connection structure such as a pipe taper screw at a position corresponding to the gap 117 .

The rear lid member 114 is airtightly attached to the rear end surface of the turret tool holder 112 by fastening means (not shown). Further, the rear cover member 114 is provided with a coolant inlet hole 119 having a connection structure with a pipe such as a tapered pipe screw. As shown in FIG. 9, the front end face of the rear lid member 114 is aligned with the guide groove formed on the cylindrical side surface of the cylindrical sliding portion 62 so as to come into contact with the rear end face of the cylindrical sliding portion 62 in the standard state. correspondingly formed. Therefore, when the rectilinear driving portion 60 performs the linear motion/indexing operation, the rear end face of the cylindrical sliding portion 62 and the front end face of the rear lid member 114 come into contact with each other, thereby stopping the backward movement of the rectilinear driving portion 60 . , to the reference state.

[Driving Means of Straight Drive Unit]
Next, the driving means of the rectilinear driving section 60 in this embodiment will be described. In the second embodiment, high pressure such as high-pressure coolant used in NC machine tools is used to perform forward and backward rectilinear motions and indexing motions of the linear drive unit 60 .

When the rectilinear drive unit 60 in the standard state as shown in FIG. At this time, the closed space 115 is filled with coolant and no pressure is supplied from the coolant inlet hole 118 of the turret tool holder 112 . Therefore, the pressure applied to the coolant inflow hole 119 advances the rectilinear driving portion 60 , and the coolant filling the closed space 115 passes through the gap 117 and is discharged from the coolant inflow hole 118 . Further, when the rectilinear driving portion 60 moves forward, the front end surface of the cylindrical sliding portion 62 and the front cover member 113 come into contact with each other, and the rectilinear driving portion 60 stops moving forward and enters the forward state. At this time, the front end surface of the cylindrical sliding portion 62 communicates with the coolant inlet hole 118 through the groove portion 120 formed in the front lid member 113 .

After that, when the rectilinear drive unit 60 in the forward state is moved backward to perform an indexing operation, high-pressure coolant is discharged from the coolant inlet hole 118 of the turret tool holder 112 .
The high-pressure coolant applies surface pressure to the front end face of the cylindrical sliding portion 62 through the groove portion 120, causing the rectilinear driving portion 60 to move backward. At this time, pressure is not supplied from the coolant inflow hole 119 of the rear lid member 114 , and the coolant filling the back of the rectilinear drive member 61 is discharged from the coolant inflow hole 119 . Further, when the rectilinear driving portion 60 moves backward, the rear end face of the cylindrical sliding portion 62 and the front end face of the rear cover member 114 come into contact with each other, and the rectilinear driving portion 60 stops moving backward and enters the reference state.

As described above, according to the second embodiment, in the standard state, the rectilinear driving portion 60 receives fluid pressure from the front end face of the cylindrical sliding portion 62 and the rear end portion is in contact with the rear lid member 114 . Standing still. Therefore, compared to the first embodiment, the force for fixing the rectilinear drive unit 60 in the front-rear direction is strong, and not only the polishing tool but also the turning tool 44 can be attached to the indexing tool holder 6 . As the turning tool 44, for example, a turning tool having a plurality of blades can be used, and by performing an indexing operation corresponding to each cutting edge of the plurality of blades, long continuous machining is possible.

As described above, according to the first and second embodiments, the coolant pressure used in the NC machine tool and the operation of the turret type tool post 100 can be used without providing special equipment. linear motion can be changed to rotary step motion. Therefore, in deburring work and polishing work by NC machine tools, it is possible to automate the rotation of polishing tools such as brushes and whetstones by an inexpensive method, and to automatically change the point of action of the polishing tools on the workpiece. , the polishing tool can be used without waste in the circumferential direction. In addition, since there is no need to manually reattach polishing tools, turning tools, etc., production efficiency can be improved.

In the above description, the case where the coolant pressure used in the NC machine tool is used as the driving means for the linear driving section was explained, but the fluid pressure for driving the linear driving section is limited to the coolant pressure. Instead, the pressure may be the pressure of hydraulic oil or the like used in general hydraulic equipment. Also, the described elements are the minimum necessary ones, and parts for functional improvement may be added and assembled as appropriate. For example, a disk-like component may be interposed between the spring support surface 16 and the return-acting elastic body 35 to eliminate the torsional force of the compression coil spring and facilitate the indexing rotation. It is clear from the description of the scope of claims that forms with such modifications or improvements can also be included in the technical scope of the present invention.

Reference Signs List 1 indexing tool holder 10 60 rectilinear driving part 11 61 rectilinear driving member 12 62 cylindrical sliding part 15 shaft part 16 spring support surface 17 inner diameter taper surface 18 screw part 19 parallel two planes 21 21 24 linear motion groove 21a 21a' 22a 22a' 24a 25a base portion 21b 21b' 22b 22b' 24b 25b tip portion 22 22' 25 inclined groove 23 step 30 indexing tool holder main body 31 pressing surface 32 116 Through hole 35 Elastic body for return action 36 Spring cap 41 Deburring tool 42 Collet 43 Collet nut 44 Turning tool 50 Stopper part 51 Sphere 52 Elastic body for sphere 53 103 Set screw 80 Sleeve 81 presser hole bottom surface 100 turret type tool post 101 106 110 112 turret tool holder 102 107 cover member 104 coolant discharge port 105 109 115 sealed space 108 118 119 coolant inlet hole 111 piston rod tip 113 front Lid member 114 Rear lid member 117 Gap 120 Groove 200 Headstock 201 Chuck.

Claims (12)

An indexing tool holder capable of converting the motion of an axially driven rectilinear drive into a rotary motion of a constant angle to change the position of the point of action of the tool,
a driving means for accommodating the linear driving portion in an indexing tool holder main body and linearly reciprocating the linear driving portion;
A guide groove engaged with a protruding member biased from the indexing tool holder body toward the linear driving portion is formed in a surface of the linear driving portion facing the indexing tool holder body,
The guide groove has a linear motion groove having a longitudinal direction parallel to the linear motion direction at the position of the indexed rotation angle, and a linear motion groove whose depth changes in a direction intersecting the linear motion direction between the indexed rotation angle. having a sloped groove with a direction and a varying depth;
The linear grooves and the inclined grooves are arranged alternately along the circumferential direction of the linear driving portion, and are continuously arranged so as to circulate in the circumferential direction on the facing surface of the linear driving portion. An indexing tool holder characterized by: The indexing tool holder of claim 1, wherein
The indexing tool holder, wherein each of the linear motion groove and the inclined groove has a base portion having the largest groove depth and a tip portion having a groove depth gradually decreasing along the longitudinal direction from the base portion. The indexing tool holder of claim 2, wherein
The indexing device, wherein the tip portion of one of the linear motion grooves and the inclined grooves is arranged continuously with the base portion of the other of the adjacent inclined grooves and the linear motion grooves. tool holder. An indexing tool holder according to claim 2 or 3,
An indexing tool holder, wherein, in a reference state, there are two or more positions in the linear motion direction of the base with which the projecting member is engaged. An indexing tool holder according to any one of claims 1 to 4,
An indexing tool holder, wherein the rectilinear drive unit includes a collet as tool fixing means and a cap for tightening the collet, and is formed with an inner diameter tapered surface for receiving the collet. An indexing tool holder according to any one of claims 1 to 5,
An indexing tool holder according to claim 1, wherein said indexing tool holder main body is provided with a return-acting elastic body for urging said rectilinear driving part in a rectilinear direction. The indexing toolholder of claim 6, wherein
The indexing tool holder, wherein the drive means advances the rectilinear drive part by fluid pressure. The indexing toolholder of claim 6, wherein
An indexing tool holder, wherein the drive means advances the linear drive portion by mechanical movement of a linear motion unit mounted on a machine tool. The indexing toolholder of claim 6, wherein
The driving means moves the turret-type tool post according to an NC program to bring the linear drive unit into contact with a fixed protrusion provided on the machine tool, thereby advancing the linear drive unit. holder. An indexing tool holder according to any one of claims 1 to 5,
The indexing tool holder, wherein the drive means advances and reverses the rectilinear drive part by fluid pressure. An indexing tool holder according to claim 7 or 10,
An indexing tool holder, wherein said fluid pressure is coolant pressure used in machine tools. An indexing tool holder according to any one of claims 1 to 11,
An indexing tool holder, wherein the tool to be mounted is a grinding tool.

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