JP3032672B2 - Taper processing device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a taper machining apparatus, and more particularly to adjustment of dynamic balance.

[0002]

2. Description of the Related Art As a taper machining apparatus, there is an apparatus for forming a tapered hole or a tapered outer peripheral surface by moving a cutting tool while rotating it. This type of taper processing apparatus is, for example, (a)
(B) a main shaft that rotates around one axis and has a slanted hole formed from the tip end surface with respect to the rotation axis;
A tool holder that is fitted into the inclined hole of the main shaft so as to be relatively movable and non-rotatable in the longitudinal direction of the inclined hole, and that holds a cutting tool at a protruding end protruding from the inclined hole; and (c) the tool holding. And a tool holder moving device for moving the body. Since the tool holder is inclined with respect to the rotation axis of the main spindle, when the tool holder is moved by the tool holder moving device, the cutting edge position of the cutting tool in the radial direction of the main spindle changes, and a tapered hole or taper is formed. The outer peripheral surface can be machined. JP-A-4-87
The taper machining device described in Japanese Patent No. 707 is one example.

[0003]

However, conventionally,
In this type of taper machining apparatus, there is a problem that a dynamic balance is not obtained, vibration occurs at the time of machining, and the machining accuracy is reduced, the life of the cutting tool is reduced, and the like. If the tool holder is moved obliquely with respect to the main axis, the position of the center of gravity of the tool holder in the radial direction of the main axis changes with the change of the cutting edge position of the cutting tool, and the dynamic balance is lost, and the above problem is solved. It will happen. According to the present invention, there is provided an apparatus for performing taper machining by moving a tool holder in a direction inclined with respect to a rotation axis of a main spindle to change a position of a cutting tool edge in a radial direction of the main spindle. An object of the present invention is to make it possible to achieve dynamic balance by a balance device having a simple structure.

[0004]

According to a first aspect of the present invention, there is provided a taper machining apparatus according to the first aspect of the present invention, wherein the (a) main shaft, (b) tool holder, and (c) tool holder moving. In addition to the device, (d) a balance piece movably fitted to the main shaft in a direction intersecting the rotation axis of the main shaft,
(E) Either the tool holder or the balance piece is formed to be inclined at a larger inclination angle with respect to the rotation axis of the main shaft in the same direction as the movement direction of the tool holder with respect to the rotation axis. And (f) an engagement projection protruding from the other of the tool holder and the balance piece and engaged with the engagement groove so as to be relatively movable in the longitudinal direction of the engagement groove. It is configured as follows.

[0005] According to a second aspect of the present invention, there is provided a taper machining apparatus.
The balance piece is movably fitted to a guide cylinder fixed to the main shaft in parallel with the movement direction of the balance piece, and an engagement protrusion is provided on the balance piece so as to be parallel to the movement direction of the balance piece on the guide cylinder. It is engaged with the engaging groove formed in the tool holder through the formed elongated hole.

According to a third aspect of the present invention, there is provided a taper machining apparatus comprising:
The engagement protrusion is configured by a pin fitted in a fitting hole formed in one of the tool holder and the balance piece, and at least one end thereof is projected from the fitting hole,
A radial bearing is arranged between at least one of the fitting hole and the engaging groove and the pin.

[0007]

In the tapering device according to the first aspect of the present invention, the position of the balance piece in the radial direction of the balance shaft changes as the tool holder is moved in the forward direction protruding from the inclined hole. Since the engaging groove is inclined at a larger inclination angle in the same direction as the direction of movement of the tool holder, the center of gravity of the balance piece moves in the radial direction opposite to the center of gravity of the tool holder. When the tool holder moves its center of gravity away from the axis of rotation of the spindle, the balance piece also moves its center of gravity away from the axis of rotation of the spindle, and the tool holder moves its center of gravity to the axis of rotation of the spindle. When the balance piece moves in a direction approaching, the balance piece also moves in a direction in which its center of gravity approaches the rotation axis of the main shaft. The balance piece moves symmetrically with respect to the rotation axis of the main shaft with respect to the tool holder (meaning that the orientation is symmetric, not necessarily symmetrical to the distance), and the dynamic unbalance generated by the movement of the tool holder. Balance is canceled or reduced.

When the balance piece is moved in a direction perpendicular to the axis of rotation of the main shaft, the balance piece moves only in the radial direction of the main shaft with the movement of the tool holder, and the dynamic balance in the radial direction of the main shaft is reduced. Be taken. When the balance piece is moved in a direction inclined with respect to the rotation axis of the main shaft, the balance piece moves not only in the radial direction of the main shaft but also in the axial direction with the movement of the tool holder. Therefore, if the moving direction of the balance piece is set so that the balance piece also advances as the tool holder is advanced, dynamic imbalance at each position in the rotation axis direction can be reduced.

The amount of movement of the balance piece accompanying the movement of the tool holder can be adjusted by selecting the inclination angle of the engagement groove and the direction of movement of the balance piece. In many cases, the unbalance amount can be kept within an allowable range in the entire movement range of the body, but if the engagement groove is formed along an appropriate curve, the movement of the tool holder in the entire movement range is possible. A good balance can be achieved.

In the taper machining apparatus according to the second aspect of the present invention, when the tool holder is moved, the movement of the engaging projection is allowed by the elongated hole, and the balance piece is guided by the guide cylinder to rotate the rotation axis of the main shaft. Move in the direction that intersects with. Therefore, for example, as described in the section of the embodiment, when the balance piece is fitted in the main shaft and is positioned in the notch formed in the tool holder, even if the balance piece moves off the main shaft and into the notch, It is guaranteed to move in a preset direction.

In the tapering device according to the third aspect of the present invention, the radial bearing reduces the relative movement resistance between the pin as the engaging projection and the engaging groove. Radial bearings
A rolling bearing such as a needle roller bearing described in the section of the embodiment may be used, or a sliding bearing may be used. In the case of a sliding bearing, a roller is fitted to a pin so as to be relatively rotatable, and can function as a sliding bearing.

[0012]

As described above, according to the first aspect of the present invention, even when the tool holder is moved in the direction inclined with respect to the rotation axis of the main shaft in order to perform taper machining, the balance piece can reduce the dynamic imbalance. Because it moves in the direction of cancellation to achieve dynamic balance, vibration during processing is reduced, processing accuracy is high,
A taper processing device having a long life of the cutting tool can be obtained.

Further, since the balance piece is linked to the tool holder by the engagement of the engagement groove and the engagement protrusion,
The balance device can be configured simply and inexpensively. In order to reduce the dynamic imbalance caused by the movement of the tool holder, it is necessary to move the balance piece in association with the movement of the tool holder, and for that purpose, a mechanism for linking the balance piece and the tool holder Although various types are conceivable, a mechanism using an engagement groove and an engagement projection is particularly simple.

According to the second aspect of the present invention, the balance piece is guided by the guide tube, and the guide tube functions as a part of the main shaft, and the main shaft is provided with balance piece guide means such as a fitting hole and a fitting groove. The formation of the balance piece guiding means is easier than in the case of direct formation. It is also possible to form the guide cylinder with a material having a lower sliding resistance than the main shaft, or to incorporate a rolling bearing,
In that case, the movement resistance of the balance piece can be reduced,
The balance piece can be accurately moved with respect to the movement of the tool holder, and the dynamic balance can be accurately obtained.

According to the third aspect of the invention, the relative movement resistance between the engagement protrusion and the engagement groove is reduced, the balance piece can be moved smoothly, and the dynamic balance can be accurately obtained. In addition, compared with the case where the engagement protrusion slides on the groove wall surface of the engagement groove, less wear is required, and the durability is improved.

[0016]

Embodiments of the present invention will be described below in detail with reference to the drawings. In FIG. 1, reference numeral 10 denotes a main shaft. Spindle 10
Has a cylindrical rotary shaft 12 rotatably supported by a frame (not shown) around its own axis, and a head main body 14 concentrically fixed to the distal end surface of the rotary shaft 12. The main shaft 10 is rotated about the rotation axis O of the rotation shaft 12 by being rotated by a rotation drive device (not shown).

The head body 14 has a circular cross section,
A radially outward flange 15 is formed at one end in the axial direction, and a fitting hole 16 is formed at the rear end face of the flange 15. A collar 17 is fitted into the fitting hole 16 and is fixed by a bolt 18, and functions as a part of the head main body 14 after being fixed. The head body 14 is positioned concentrically with the rotary shaft 12 by fitting the collar 17 into the center hole of the rotary shaft 12, and the relative phase is determined by the pin 20, and the head 22 is
To the rotating shaft 12. The head body 14 can be understood to be a member constituting the main shaft 10 together with the rotary shaft 12 as described above, but from a different viewpoint, the rotary shaft 12 is the main shaft, and the head main body 14 is Can be considered as a body of a tapered head that is detachably attached to the tip of the head.

An inclined hole 26 is formed in the head main body 14 so as to open at the front end face of the head main body 14, that is, the front end face 24 of the main shaft 10, and is inclined with respect to the rotation axis O of the main shaft 10. As shown in FIG. 2, the inclined hole 26 has a substantially rectangular cross section, and the tool holder 30 is fitted therein. The cross-sectional shape of the tool holder 30 is a rectangle smaller in size than the inclined hole 26, and is fitted into the inclined hole 26 via the spacers 32, 34, 36 so as to be relatively movable in the longitudinal direction of the inclined hole 26 and relatively non-rotatable. Have been combined.

The spacer 32 has a thin plate shape as shown in FIGS. 1 and 2, is slightly shorter than the length of the inclined hole 26, and is formed between one side surface of the tool holder 30 and one inner wall surface of the inclined hole 26. It is sandwiched between. These one side and one inner wall are
This plane is parallel to the moving direction of the tool holder 30 and orthogonal to the reference plane P (see FIG. 2) including the rotation axis O of the main shaft 10. A notch 38 is formed in a rear portion (a portion on the side of the rotating shaft 12) of the spacer 32, and forms a forked shape as shown in FIG. Although not shown, an oil groove is formed on the surface of the spacer 32 that contacts the tool holder 30. The oil groove communicates with an oil passage 40 (see FIG. 1) formed in the head main body 14 and is supplied with lubricating oil, and a large number of oil grooves branched from the main oil groove over the entire spacer 32. And a lubricating oil is supplied between the groove and the tool holder 30 to lubricate the sliding surface of the tool holder 30.

Similarly, the spacer 34 has a thin plate shape, is slightly shorter than the length of the inclined hole 26, and is formed between the surface parallel to the reference plane P of the tool holder 30 and the inner wall surface of the inclined hole 26 opposed thereto. It is sandwiched between. An oil groove is also formed on the surface of the spacer 34 that contacts the tool holder 30 so that the head body 14
Lubricating oil is supplied from an oil passage (not shown) formed in
The sliding surface of the tool holder 30 is lubricated.

The spacer 36 has an elongated plate shape, is slightly shorter than the length of the inclined hole 26, and is formed between the tool holder 30 and the head body 14 in a posture inclined with respect to the reference plane P as shown in FIG. It is sandwiched between. As shown in FIG.
As shown in FIG. 5, an oil groove 41 is formed on the surface that is brought into contact with the tool holder 30, and an engagement groove 42 is formed at one longitudinal end of the spacer 36. The head 46 of the screw 44 is engaged with the engagement groove 42.
The spacer 36 is prevented from coming out of the head main body 14 by being engaged with.

As shown in FIG. 4, the thickness of the spacer 36 is gradually reduced toward an end opposite to the side where the screw 44 is engaged, and an inclined surface 48 is formed at the end. 3, the spacer 36 is pressed against the tool holder 30 by a frame 50 fitted to the rear part of the head body 14. As shown in FIG. The top 50 has an inclined surface 48.
Is formed, and the inclined surface is pressed against the inclined surface 48 of the spacer 36 by the screw 52, the spacer 36 is pushed toward the tool holder 30, and the tool holder 30 is , 34 side.

As shown in FIG. 1, a cutting tool 56 for finishing is detachably attached to the projecting end of the tool holder 30 projecting from the inclined hole 26. Cutting tool 56
Has a tip holder 58 and a tip 60 fixed to the tip holder 58, and fits into a fitting hole 64 formed in the tool holder 30 at a fitting portion 62 having a circular cross section provided on the tip holder 58. The pin 66 determines the relative phase with respect to the tool holder 30 and is fixed by the set screw 68 (see FIG. 2). The cutting tool 56 is attached to the tool holder 30 and the tool holder 30 is
When moved in the forward direction protruding from the
The zero cutting edge is fixed at a position near the rotation axis O of the main shaft 10.

At the rear end of the tool holder 30 opposite to the side to which the cutting tool 56 is fixed, as shown in FIG. 1, the collar 17 is held via a bush 72 so as to be movable in the axial direction. The moving member 74 is engaged. Tool holder 3
1 and 5, an engagement groove 76 having a T-shaped cross-section and extending in a direction parallel to the reference plane P and perpendicular to the rotation axis O of the main shaft 10, as shown in FIGS. Are formed.

The moving member 74 has a moving shaft 80 having a circular cross section, and an engaging member 82 fixed to one end of the moving shaft 80. As shown in FIGS. 1 and 6, the engaging member 82 has a dimension T slidably engageable with the engaging groove 76.
It has a plate-shaped engaging portion 84 longer than the diameter of the moving shaft 80 and shorter than the engaging groove 76, and a leg 86 protruding from the engaging portion 82. It is fixed to the moving shaft 80. The engaging member 82 abuts on the bottom surface of the engaging groove 76 on a wide surface, and does not give a twisting moment to the tool holder 30, and the tool holder 30 is
The tool holder 30 can be moved forward while allowing light sliding in a direction perpendicular to the axis of the moving shaft 80 with respect to. The moving shaft 80 projects through the collar 17 and the bush 72 into the rotating shaft 12,
It can move on the rotation axis O of zero.

At the end of the moving shaft 80 on the side protruding into the rotary shaft 12, a small diameter engaging shaft portion 96 is protruded concentrically, and an engaging portion 98 having a larger diameter than the engaging shaft portion 96 is provided. Is formed between the engaging portion 98 and the moving shaft 80.
00 is formed. A drive shaft 102 provided in the rotation shaft 12 so as to be relatively movable and relatively rotatable in the axial direction is engaged with the engagement groove 100. Drive shaft 10
2 has an engaging portion 104 protruding radially inward from the inner peripheral surface of the center hole opened at the tip. This engaging part 1
04 can pass through the engaging portion 98 in the axial direction in a specific phase, and is rotated by a certain angle after passing through the engaging portion 98 and reaching the engaging groove 100, so that the engaging portion 98 separates the engagement portion 98. Engage with the engagement groove 100 in the prevented state.

The drive shaft 102 is connected to a rotary drive (not shown) for disengagement from the engaging portion 98 and also to an axial drive (not shown) using a stepping motor as a drive source. I have. In the present embodiment, the rotary drive device and the axial drive device are provided so as not to rotate, and are connected to the drive shaft 102 in a state that allows the drive shaft 102 to rotate together with the main shaft 10. At least one of them can be provided so as to rotate with the main shaft.

In order to avoid interference with the engaging member 82 when the moving member 74 moves forward, as shown in FIGS.
Are formed. A notch 110 is formed along the reference plane P at a position on the rotation axis O of the main shaft 10 of the tool holder 30 as shown in FIGS. Notch 110 is formed through tool holder 30,
The tool holder 30 has openings on two side surfaces perpendicular to the reference plane P.

Since the dynamic balance of the assembly of the head body 14 and the tool holder 30 is greatly disturbed due to the formation of the above-mentioned clearance groove 106, notch 110, etc., in order to compensate for this,
A balance section 111 is provided on the head body 14.
The balance portion 111 is provided as a protrusion protruding outward in the radial direction from the outer peripheral surface of the head main body 14, and is provided near the end of the inclined hole 26 on the side near the rotating shaft 12. This balance unit 111 is also used as a material removing unit for final dynamic balance adjustment, as described later.

Even if the assembly of the head body 14 and the tool holder 30 is dynamically balanced by the formation of the balance portion 111, the center of gravity of the tool holder 30 is rotated by the tool holder 30 if the tool holder 30 advances. Since the dynamic balance is lost near the axis O, a balance device 112 is provided to reduce the dynamic balance. Hereinafter, the balance device 112 will be described.

Each of a pair of side walls 113 (see FIG. 5) located on both sides of the notch 110 of the tool holder 30 moves the tool holder 30 with respect to the rotation axis O of the main shaft 10. The engagement groove 114 is formed to be inclined at a larger inclination angle in the same direction as the inclination direction of the direction.

When the tool holder 30 is at the retracted end position where the amount of protrusion from the inclined hole 26 is the smallest, the head body 14
At a position corresponding to the front end of the notch 110,
0 is provided. The guide cylinder 120 is fitted so as to be movable in a direction perpendicular to the rotation axis O of the main shaft 10 and parallel to the reference plane P, and the balance piece 122 is fitted to the guide cylinder 120 so as to be movable in the same direction. Have been. The guide tube 120 penetrates through the spacer 32 and has the notch 1
10 are fitted so as to be relatively movable, and both end portions are fitted into fitting holes of the head body 14. This guide tube 1
20 at two places facing the side wall 113, respectively.
An elongated hole 124 is formed in parallel with the moving direction of the balance piece 122.

A pin 130 is fitted to the balance piece 122 via a needle roller bearing 132 in a direction perpendicular to the rotation axis O of the main shaft 10 and the moving direction of the balance piece 122. The pin 130 has a diameter capable of penetrating the elongated hole 124 without contacting the side wall surface of the elongated hole 124. Both ends of the pin 130 protruding from the guide cylinder 120 are formed on the tool holder 30, respectively. The engagement groove 114 is relatively movably engaged.

As shown in FIG. 7, the pin 130 is shorter than the width of the tool holder 30 and has both ends formed with engagement grooves 114, respectively.
Does not protrude from the tool holder 30 and does not hinder the movement of the tool holder 30. The pin 130 is fitted to one end of the balance piece 122 in the movement direction, and is engaged with the vicinity of the front end of the engagement groove 114 when the tool holder 30 is at the retracted end position as shown in FIG. At the same time, substantially the entire balance piece 122 is located on one side of the rotation axis O of the main shaft 10.

When the tool holder 30 moves upward in FIG. 1 in a direction perpendicular to the rotation axis O as it advances, the balance piece 122 moves downward due to the effect of the slope of the engaging groove 114. When the tool holder 30 moves to the advanced end position as shown in FIG. 8, almost the entire balance piece 122 is located on one side of the rotation axis O opposite to that in FIG. The tool holder 30 and the balance piece 122 are moved symmetrically with respect to the rotation axis O in the diameter direction of the main shaft 10.

When the balance piece 122 is moved, the guide cylinder 120 guides the movement of the balance piece 122 while avoiding interference with the pin 130, and is rotatable by the balance piece 122 via the needle roller bearing 132. The held pin 130 moves while rolling in the engagement groove 114.

The pin 130 is, as shown in FIG.
From the pin insertion hole 136 formed in the head body 14 through the through hole 138 formed in the spacer 34, the engagement groove 11
4, the needle roller bearing 132 attached to the long hole 124 and the balance piece 122 is inserted. Pin 132
In a state in which the balance piece 122 is positioned at a position where the needle roller bearing 132 matches the pin insertion hole 136, and the tool holder 30 is moved to a position where the elongated hole 124 matches the pin insertion hole 136. After insertion, the pin insertion hole 136 is closed by the plug 142. The tip of the plug 142 is inserted into the through hole 13 of the spacer 34.
8 and serves to prevent displacement of the spacer 34, and its tip end surface is located on the same plane as the surface of the spacer 34 on the tool holder 30 side, and the pin 130 moves toward the through hole 138. To block. When removing the pin 130, the plug 142 is removed, and the external thread of the removal tool is screwed into the female screw hole 146 formed at the end of the pin 130,
Pull out the pin 130.

As is clear from the above description, the engagement groove 1
14, pin 130, needle roller bearing 132, guide cylinder 12
0, the balance device 112 by the balance piece 122 and the like.
The head body 14, the tool holder 30, the balance device 112, etc.
48 are configured.

Next, the dynamic balance adjustment of the tapering head 148 by the balance device 112 will be described. To adjust the dynamic balance, the taper processing head 148 is
, And attach it to a balancing machine.
First, a dynamic balance is obtained in a state where the tool holder 30 is moved to an intermediate position in the moving range. Since the balance portion 111 is formed to be slightly excessively large, a balance piece of various masses can be attached to a position on the opposite side of the balance portion 111 of the head main body 14 with a gum tape or the like to achieve dynamic balance.

From this state of dynamic balance, the tool holder 30 is moved to the forward end position by a set distance (for example, 5 mm), and the dynamic unbalance amount is measured each time the tool holder 30 is moved. In addition, it is moved by a set distance from the intermediate position to the retreat end position, and the imbalance amount is measured each time it is moved. Then, the mass of the balance piece at a position opposite to the balance portion 111 is adjusted so that the unbalance amounts at all the measurement points are of an acceptable size. Thereafter, the adjusted balance piece is tapered to the taper processing head 148.
, The mass of the balance piece is measured, and the same amount of material is removed from the balance portion 111 by cutting, so that the tapered processing head 148 is in a dynamic balanced state.

When a taper hole is machined by the present taper machining apparatus, the workpiece 150 shown in FIG. 9 is set at a predetermined position by a holding jig (not shown). The holding jig is manufactured so that the workpiece 150 is at the relative position shown in FIG. 9 with respect to the cutting tool 56 at the retracted end position together with the tool holder 30. A straight hole 154 is formed in the work piece 150 as a prepared hole of the tapered hole 152, and the cutting tool 56 advances to a cutting feed start position that is a small distance away from the work piece 150 by rapid feeding of the tool holder 30. Let me do. At this rapid traverse, even if the spindle 10 is rotated,
You don't have to.

Next, the cutting tool 56 is advanced by a speed (cutting feed speed) suitable for machining while being rotated by the rotation of the main shaft 10, and cuts the tapered hole 152. After the cutting tool 56 is advanced to the machining end position where the machining of the entire tapered hole 152 is completed, the cutting tool 56 is returned to the retracted end position by rapid traverse while being rotated.

The moving range of the cutting edge of the tip 60 of the cutting tool 56 is determined from the retracted end position to the advanced end position shown in FIG. 9, and the cutting edge of the tip 60 at the retracted end position and the tip 60 at the advanced end position. A taper hole corresponding to a part of a tapered surface which is a trajectory of a straight line when the straight line connecting the cutting edge of the main shaft 10 is rotated around the rotation axis O of the main spindle 10 is formed into a tapered hole having various diameters. It can be processed with equipment. The relative position in the axial direction of the workpiece 150 with respect to the forward end position may be changed in various ways, and this change in relative position can be realized by preparing a plurality of types of holding jigs.

In the present taper machining apparatus, the amount of dynamic unbalance is adjusted to an allowable level over the entire moving range of the tool holder 30, so that vibration during cutting is small and the tapered hole 152 can be accurately formed. Can be processed.

Further, since the pin 130 is fitted to the balance piece 122 via the needle roller bearing 132, the pin 130 has low rotational resistance and moves while rolling on the side wall surface of the engagement groove 114 of the tool holder 30. As a result, the balance piece 122 is moved to an accurate position, the dynamic balance is favorably maintained, and the machining accuracy is improved in this respect as well.

Further, the balance piece 122 is moved by passing through the notch 110 of the tool holder 30. Since this movement is guided by the guide cylinder 120, the balance piece 122 is balanced even when the entire balance piece 122 reaches the notch 110. It is ensured that the piece 122 does not rotate around the pin 130 and moves only in a direction perpendicular to the rotation axis O of the main shaft 10. Although it is not impossible to provide a portion for forming the fitting hole of the balance piece 122 in the head body 14 itself, the shape of the head body 14 becomes complicated and processing becomes troublesome. As in this embodiment, the guide tube 1
If the head 20 is manufactured separately from the head main body 14 and later fixed to the head main body 14 so as to function as a part of the head main body 14, the processing of the head main body 14 is simplified.

As is clear from the above description, in this embodiment, the drive shaft 102, a stepping motor as a rotary drive source which is a kind of drive source, and the movement of the drive source are converted into the axial movement of the drive shaft 102. The motion converting mechanism and the like constitute a tool holder moving device, and the needle roller bearing 132 constitutes a radial bearing.

In the above embodiment, the balance piece 122 is arranged in the notch 110 of the tool holder 30, but as shown schematically in FIGS.
A balance piece 162 may be provided outside the tool holder 160.

The tool holder 160 is fitted into the inclined hole 165 inclined with respect to the rotation axis O of the main shaft 164 so as to be relatively movable and non-rotatable.
Is attached to the tool holder 160 at a position away from the rotation axis O as the tool holder 160 advances. The embodiment shown in FIGS. 1 to 9 is different from the embodiment shown in FIGS.

As shown in FIG. 11, the balance piece 162 has guide grooves having a rectangular cross section formed in directions inclined with respect to the rotation axis O of the main shaft 164 at positions on both sides of the tool holder 160 of the main shaft 164, respectively. 167 so as to be movable. The balance piece 162 includes the tool holder 1
An engagement groove 168 inclined at a larger inclination angle is formed in the same direction as the inclination direction of the moving direction of the tool holder 60.
Both ends of the pin 170 protruding from the tool holder 160 are inserted into the rollers 1 as radial bearings.
72 are engaged.

Therefore, as the tool holder 160 is moved, the two balance pieces 162 are also moved, but the main shaft 16 of the balance piece 162 is moved.
4 with respect to the rotation axis O, the tool holder 160
The balance piece 162 is also set so as to move forward when moving forward. The engagement groove 168 is provided in the tool holder 160.
Is located at the retracted end, the pin 170
The roller 172 is formed at a position where it engages with a portion near the rear end of the engagement groove 168.

In the present taper machining apparatus, the tool holder 16
When 0 is advanced, the tool holder 160 moves upward in FIG. 10, and the balance piece 162 moves downward. Thereby, the dynamic imbalance in the radial direction of the main shaft 164 caused by the movement of the tool holder 160 is reduced. In addition, in this embodiment, the tool holder 1
Since the balance piece 162 advances as the 60 advances, the occurrence of dynamic imbalance at each position along the rotation axis O of the main shaft 164 is also well avoided.
Even if the tapered head as a whole is in dynamic balance, for example, if the dynamic balance at each of the front end and the rear end deteriorates, the tapered head vibrates. The longer the moving distance, the more noticeable. Therefore, when the tool holder has a long moving distance in the axial direction, it is desirable that when the tool holder advances, the balance piece moves forward while maintaining the dynamic balance.

When the balance piece 162 is provided outside the tool holder 160, the movement direction of the balance piece 162 and the tool holder 16
Although a dynamic imbalance occurs in a direction perpendicular to the movement direction of 0, in this embodiment, since the balance pieces 162 are provided symmetrically on both sides of the tool holder 160, the movement of each balance piece 162 is caused. The resulting dynamic imbalances in the above directions are opposite to each other and cancel each other, and the dynamic balance is improved.

However, it is not essential to provide two balance pieces symmetrically outside the tool holder, and only one balance piece may be provided. The dynamic imbalance in the direction perpendicular to the moving direction of the balance piece 162 and the moving direction of the tool holder 160 is secondary, and the primary dynamic imbalance is to use one balance piece with a tool. It can be removed simply by providing it outside the holder.

In each of the above embodiments, the tool holder 3
The dynamic unbalance amount is measured at a plurality of locations within the movement range of 0, 160, and based on the measurement result, the dynamic unbalance amount is set to an allowable size in the entire movement range of the tool holders 30, 160. The amount of material cut off of the balance portion 111 was determined, but the engagement grooves 114 and 1 were determined based on the measurement results.
The dynamic balance can be obtained by changing the position, direction, and shape of 68. In this case, it is necessary to remake the tool holder 30 and the balance piece 162. Therefore, it is preferable to form an engagement groove on the simple side of the structure of the two, and in general, to form the engagement groove on the balance piece side. Is good. When the shape of the engagement groove is changed, it is preferable to first form a linear engagement groove and change the shape along an appropriate curve based on the measurement result.

In each of the above embodiments, the spindle 10,
Although the dynamic balance is achieved by removing a part of the material of 164, the dynamic balance can be achieved by fixedly adding a balance piece to the main shaft. In this case, if the balance piece is made detachable, dynamic balance can be obtained by adding or replacing the balance piece, and even if material is removed by cutting, removing the balance piece and cutting will make it easier to work. Become. Further, dynamic balance can be obtained by changing the mass of the balance pieces 122 and 162 or the tool holders 30 and 160 that are linked to the tool holders 30 and 160.

Furthermore, by determining the shape and dimensions of each component of the taper machining apparatus by calculation using a computer or the like, it is possible to balance the dynamics at the design stage. For example, in the embodiments shown in FIGS. 1 to 9, if the tentative shapes and dimensions of the head body 14, the tool holder 30, the balance piece 122, etc. are determined, their product of inertia is calculated, and their assemblies are assembled. Taper processing head 14
8, one of the principal axes of inertia passing through the center of gravity is the rotation axis O of the spindle 10.
The head body 14, the tool holder 30,
At least one shape and size of the balance piece 122 and the like are changed. Note that the change in the shape and dimensions includes the position, direction, and shape of the engagement groove 114.

As in the embodiment shown in FIGS. 1 to 9, the pin 130 is rotatably fitted in a fitting hole formed in the balance piece 122 and
When at least one end protruding from the pin is engaged with the engaging groove 114 formed in the tool holder, a radial bearing such as a needle roller bearing 132 is provided between the pin 130 and the fitting hole. Or in addition to the engagement groove 11
A radial bearing may be provided between the pin 4 and the pin 130.
As in the embodiment shown in FIGS. 10 and 11, the pin 170 is rotatably fitted into the fitting hole formed in the tool holder 160, and at least one end protruding from the tool holder 160 is fitted to the balance piece 162. When engaged with the formed engaging groove 168, the pin 170 and the engaging groove 1
A radial bearing such as a roller 172 may be provided between the pin 170 and the tool holder 160 instead of or in addition to the radial bearing.

In each of the above embodiments, the pin is provided through the balance piece or the tool holder, and both ends of the pin projecting from the balance piece or the tool holder constitute engagement projections. Has the advantage of being easy to manufacture, but is not limited to this, for example,
A short pin may be fitted into a fitting hole formed in the balance piece or the tool holder to form an engaging projection. In this case, the pin may be fixed to a balance piece or a tool holder, or may be supported via a radial bearing. Further, the engagement projection may be provided integrally with the balance piece or the tool holder. When fixing the engagement projection to the balance piece or the tool holder, a radial bearing is provided between the engagement projection and the engagement groove. It is also possible to omit the radial bearing.

In the embodiment shown in FIGS. 1 to 9, the notch 110 formed in the tool holder 30 is formed so as to penetrate the tool holder 30. 14, the guide tube 1
There is an advantage that the support of the support 20 is stable, but the notch may be a concave portion having one end closed. In this case, if it is necessary to provide a guide cylinder, it may be supported on the main shaft in a cantilever manner and relatively moved in the recess.

Further, in the embodiment shown in FIGS. 1 to 9, the guide tube 120 is fitted to the main shaft 10 to guide the movement of the balance piece 122, so that the guide means of the balance piece 122 can be easily provided. However, a guide cylinder may be provided integrally with the main shaft 10. In this case, for example, a notch provided in the tool holder may be opened also on the rear end face to avoid interference with the guide cylinder.

In each of the above embodiments, the tool holder 3
The reference numerals 0 and 160 have a rectangular cross section, and the non-circular cross section serves as a rotation transmitting means for transmitting the rotation of the spindles 10 and 164 to the tool holders 30 and 160. However, it is also possible for the tool holder to have a circular cross section. In this case, a separate rotation transmitting means for transmitting the rotation of the main shaft to the tool holder is provided.

The present invention provides a taper machining device for roughing a tapered hole in a workpiece, a taper machining device for roughing or finishing a tapered outer peripheral surface, and a spindle and a workpiece parallel to a rotation axis of a spindle. The present invention can also be applied to a taper processing device having an axial moving device for relatively moving in a desired direction.

Further, the inventions according to claims 1 to 3 can be implemented by combining the components of the above embodiments with each other. In addition, without departing from the scope of the claims,
The present invention can be implemented in various modified and improved embodiments based on the knowledge of those skilled in the art.

[Brief description of the drawings]

FIG. 1 is a front sectional view showing a taper machining apparatus according to an embodiment common to the first to third aspects of the present invention.

FIG. 2 is a left side view of the taper processing device.

FIG. 3 is a right side view showing a head main body and a tool holder constituting a main shaft of the taper processing device, with a collar removed.

FIG. 4 is a front view showing a spacer sandwiched between a tool holder and a head body of the taper processing device.

FIG. 5 is a plan view showing a tool holder of the taper processing device.

FIG. 6 is a plan view showing a moving member of the taper processing device.

FIG. 7 is a sectional view taken along line VII-VII in FIG.

FIG. 8 is a front sectional view showing a state in which the tool holder of the taper processing device has been moved to a forward end position.

FIG. 9 is a diagram illustrating taper hole processing by the taper processing device.

FIG. 10 is a view schematically showing a taper processing apparatus according to another embodiment of the first and third aspects of the present invention, and is a sectional view taken along line XX in FIG. 11;

11 is a left side view schematically showing the taper processing device shown in FIG.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 10 Main shaft 24 Tip surface 26 Inclined hole 30 Tool holder 56 Cutting tool 74 Moving member 102 Drive shaft 114 Engagement groove 120 Guide cylinder 122 Balance piece 124 Long hole 130 Pin 132 Needle roller bearing 160 Tool holder 162 Balance piece 164 Main shaft 165 Inclined hole 166 Chip 168 Engagement groove 170 Pin 172 Roller

────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Michitaka Okukawa 1 Toyota Town, Toyota City, Aichi Prefecture Inside Toyota Motor Corporation (56) References JP-A-4-122504 (JP, A) JP-A-4-87707 (JP, A) JP-A-1-171707 (JP, A) JP-A-2-95505 (JP, A) JP-A-52-137788 (JP, A) JP-A-5-345205 (JP, A) 1979-10893 (JP, U) 1987-39903 (JP, U) (58) Fields investigated (Int. Cl. ⁷ , DB name) B23B 29/034 B23Q 11/00

Claims (3)

(57) [Claims] 1. A main shaft which rotates about one axis and has an inclined hole formed from a tip end surface with respect to the rotation axis, and a movable and relatively movable inclined hole of the main shaft in a longitudinal direction of the inclined hole. A tool holder that is non-rotatably fitted and holds a cutting tool at a protruding end protruding from the inclined hole, a tool holder moving device that moves the tool holder, and the main shaft intersects a rotation axis of a main shaft. A balance piece fitted movably in a direction, an inclination direction of a moving direction of the tool holder with respect to a rotation axis of the main shaft with respect to one of the tool holder and the balance piece. An engagement groove formed to be inclined at a larger inclination angle in the same direction as the above, and protrudingly provided on the other of the tool holder and the balance piece, relative to the engagement groove in a longitudinal direction of the engagement groove. Moveable Tapering device which comprises an engaging projection which is engaged with. 2. The balance piece is movably fitted to a guide cylinder fixed to the main shaft in a direction parallel to the direction of movement of the balance piece, and the engaging projection is provided on the balance piece so as to protrude therefrom. The taper machining device according to claim 1, wherein the taper machining device is engaged with an engagement groove formed in the tool holder through an elongated hole formed in the cylinder in parallel with the movement direction of the balance piece. 3. A pin having the engaging projection fitted in a fitting hole formed in one of the tool holder and the balance piece, and having at least one end protruding from the fitting hole. The taper machining device according to claim 1, wherein a radial bearing is provided between at least one of the fitting hole and the engagement groove and the pin.