JP2000233344A - Angular head capable of position indexing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a position indexing angular head capable of adjusting indexed positions of a cutting tool by a simple structure. SOLUTION: When a main spindle 5 is rotated normally (in F direction), torque is transmitted in the order of a power shaft 4, bevel gears 13, 14 to rotate a tool rotating shaft 8 in the direction of cutting, and then cutting is performed by a cutting tool 9. At this time, a one-way clutch 16 does not transmit torque. On the other hand, when the main spindle 5 is rotated reversely (in R direction), the one-way clutch 16 transmits torque to a harmonic drive 20. When a flexual spline 18 is rotated, a rotating casing 12 is rotated around the power shaft 4. Thus, the position-indexing of the tool rotating shaft 8 and the cutting tool 9 is performed.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an angular head that can be indexed for use in angle head processing by a machine tool such as a machining center.

[0002]

2. Description of the Related Art For example, in a machining center, an angular head is used for angle head processing such as side processing, inner surface processing, or inclined surface processing of a work. This angular head has a base end side coaxially mounted on a main shaft of a machining center and a cutting tool extending and attached to a front end side in a direction intersecting the main shaft. Then, with the cutting tool fixed at a predetermined indexing position, the spindle is rotated to process the work.

In angle head machining, when there are a plurality of machining locations on the periphery of a work, it is necessary to change the indexing position (direction) of the cutting tool. As a conventional example, an angular head having a structure in which the indexing position is manually changed is commercially available.In this structure, for example, the indexing position is adjusted after loosening the tightening bolt and once removing the angular head from the machine tool. It is necessary to perform work such as mounting it on the machine tool again and tightening the tightening bolt, which is troublesome, and requires a long time for adjustment,
There is a problem that work efficiency is reduced.

In order to solve the above problem, an angular head (angular attachment) capable of adjusting the direction of a cutting tool accurately in a short time while being mounted on a main shaft of a machine tool is disclosed in Japanese Patent Laid-Open No. 6-55395. No. 6,086,045. In this angular head, a power shaft provided in a casing and a tool rotation shaft are connected via a power transmission mechanism. The casing is composed of a fixed casing that is prevented from rotating around the spindle head of the machine tool, and a rotating casing that supports the tool rotating shaft. The upper casing is provided on the fixed casing so as to be able to move up and down and is urged downward by a spring. On the other hand, the lower casing is provided on the rotating casing, and the rotating casing is prevented from rotating by the engagement of the upper and lower carriers.
The upper car vic is raised and lowered by a hydraulic cylinder via a positioning pin and a lever. The rotating casing is coupled to the power shaft when the upper and lower carbics are disengaged by the operating mechanism, and is released from the power shaft when the upper and lower carbics are engaged.

Therefore, when the upper and lower carbics are dissociated, the rotary casing is rotatable and connected to the power shaft. When the power shaft is rotated in this state, the rotary casing rotates to a predetermined index angle, and the tool rotation axis, that is, the direction of the cutting tool is automatically adjusted.

However, this angular head has a problem that the operating mechanism is composed of a plurality of parts and a hydraulic circuit is required because a hydraulic cylinder is used, so that the structure is complicated. Further, indexing can be performed only by an integral multiple of the number of teeth (the number of divisions) of the Carvic coupling, and for example, indexing at 45 ° and 42 ° is impossible.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned conventional drawbacks, and an object of the present invention is to provide an indexable angular head capable of adjusting the indexing position of a cutting tool with a simple structure. To provide.

[0008]

Means and Effects for Solving the Problems Claim 1
The angular head whose position can be indexed is arranged with a power shaft 4 coaxially mounted on a main shaft 5 of the machine tool which can be driven forward and reverse, and arranged in a direction intersecting the power shaft 4 and a cutting tool 9. A tool rotating shaft 8 to which the tool is attached, power transmission mechanisms 13 and 14 for transmitting forward rotation force from the power shaft 4 as power in the cutting direction to the tool rotating shaft 8, and a tool for supporting the tool rotating shaft 8; A rotating casing 12 rotatably arranged around the power shaft 4, a main driving shaft connected to the power shaft 4, and when the power shaft 4 rotates forward, the driven shaft is stationary while the power shaft is stationary. When the shaft 4 rotates in the reverse direction, the one-way clutch 16 rotates the driven shaft.
When the driven shaft of the one-way clutch 16 is stationary, the rotation of the rotary casing 12 is stopped, while when the driven shaft rotates, the rotary casing 1 is stopped.
It is characterized by having transmission braking mechanisms 20 and 21 for rotating the two in conjunction with each other.

In the angular indexable head according to the first aspect of the present invention, the main shaft 5 of the machine tool is rotated forward and the power shaft 4 is rotated.
Is rotated forward, the forward rotation force from the power shaft 4 is applied to the tool rotation shaft 8 to which the cutting tool 9 is attached, by the power transmission mechanism 13,
The tool rotation shaft 8 rotates in the cutting direction, and is cut by the cutting tool 9 into the workpiece. At this time, since the driven shaft of the one-way clutch 16 connected to the power shaft 4 is in a stationary state, the rotating force from the one-way clutch 16 is not transmitted to the rotating casing 12 that supports the tool rotating shaft 8, and the power is transmitted. Braking mechanism 20, 2
1 stops at a predetermined position. That is, the cutting tool 9 is set at a predetermined indexing position.

On the other hand, when the main shaft 5 of the machine tool is reversed and the power shaft 4 is reversed, the driven shafts of the one-way clutch 16 rotate in conjunction with each other.
Rotates the rotary casing 12 in conjunction with the driven shaft. Therefore, the cutting tool 9 can be automatically rotated to a desired indexing position.

As described above, according to the angular indexable head according to the first aspect, the indexing position of the cutting tool 9 is adjusted by using the rotational force of the main shaft 5 of the machine tool. This eliminates the need for another driving device, and can be realized at a low cost with a simple structure. The transmission braking mechanisms 20 and 21 described above are the one-way clutch 16
When the driven shaft of the rotary casing 12 is stationary,
And a transmission means 20 for interlockingly rotating the rotating casing 12 when the driven shaft rotates, and the one-way clutch 16 is directly connected to the rotating casing 12. in case of,
The transmission means 20 is constituted by the direct connection structure.

According to a second aspect of the present invention, there is provided an angular head capable of indexing a position, wherein the transmission braking mechanism uses a braking means which operates with a cutting fluid supplied to the cutting tool as a working fluid. It is characterized by stopping rotation.

In the angular indexable head according to the second aspect, it is not necessary to externally supply a dedicated power (working fluid) for operating the braking means 21.
This can also simplify the structure.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, a specific embodiment of an angular head capable of indexing position according to the present invention will be described in detail with reference to the drawings. FIG. 1 is a side sectional view showing the structure of the angular head 1a according to the first embodiment, and FIG. 2 is a front view schematically showing the vicinity of a tool rotation shaft 8.

The angular head 1a has a power shaft 4 rotatably mounted on a fixed casing 2 by bearings 3. The power shaft 4 has a tapered connection 4 at its base end.
a, and is fitted coaxially to the main shaft 5 by fitting the tapered connection portion 4a to a tapered connection portion 5a formed at the tip of a main shaft 5 provided in a machine tool such as a machining center. On the other hand, the fixed casing 2 is fixed to the cutting fluid supply bracket 7 provided in the machine tool by the detent pin 6.

A tool rotating shaft 8 is disposed on the tip side of the power shaft 4 so as to extend in a direction substantially perpendicular to the power shaft 4. The tool rotating shaft 8 has a cutting tool 9 attached to the distal end side and a base end side rotatably attached to a rotating casing 12 by bearings 10 and 11. The bevel gear 13 attached to the tip of the power shaft 4 and the bevel gear 14 inserted into the tool rotation shaft 8 mesh with each other, whereby the rotational force of the main shaft 5 is reduced by the power shaft 4 and the bevel gear 13. , 14 to the tool rotation shaft 8, and the cutting tool 9 rotates.
The rotating casing 12 is attached to the distal end side of the power shaft 4 by a bearing 15 so as to be rotatable around the same axis as the power shaft 4.

Further, a one-way clutch 16 is connected to the power shaft 4. The one-way clutch 16 has a main driving shaft connected to the power shaft 4, and a wave generator 17 fixed to the driven shaft. The wave generator 17 is fitted with a flexspline 18, and the flexspline 18 is mechanically fastened to the rotary casing 12 by bolting or the like. The flex spline 18 is meshed with the circular spline 19,
The circular spline 19 is mechanically fastened to the fixed casing 2 by bolting or the like. The wave generator 17, the flex spline 18, and the circular spline 19 are a harmonic drive (registered trademark).
20. This harmonic drive 20
Functions as a reduction gear.

The one-way clutch 16 is connected to the power shaft 4
When the motor rotates forward (in the direction of arrow F), the driven shaft is kept stationary, while when the power shaft 4 rotates in the reverse direction (in the direction of arrow R), the driven shaft is rotated in conjunction therewith. Therefore, the rotational force is transmitted to the wave generator 17 only when the power shaft 4 reverses.

The fixed casing 2 is provided with a disc brake 21.
The rotation of the flexspline 18, that is, the rotation of the rotary casing 12 is stopped by 1. This disc brake 2
Numeral 1 is configured to operate with the cutting fluid supplied from the cutting fluid supply bracket 7 as a working fluid. In the present embodiment, the harmonic drive 20 and the disc brake 21 constitute a transmission braking mechanism.

The operation of the angular head 1a having the above configuration at the time of cutting will be described. Turn the spindle 5 in the forward direction (arrow F
), The power shaft 4 and the bevel gear 13 also rotate forward, and accordingly, the bevel gear 14 and the tool rotating shaft 8 rotate in the cutting direction C, and at the same time, the cutting tool 9 also rotates in the cutting direction C. A cutting process can be performed on a work (not shown).

At this time, since the one-way clutch 16 does not transmit the rotational force to the wave generator 17, the rotary casing 12 does not rotate. Further, a force for rotating the rotary casing 12 around the power shaft 4 acts on the rotary casing 12 by a reaction force of the cutting force.
Are mechanically fastened to the flexspline 18, and the flexspline 18 is fixed to the fixed casing 2 by the disc brake 21, so that the rotating casing 12 does not rotate.

Next, the operation when the position of the cutting tool 9 is determined will be described. After the machining by the cutting tool 9, the supply of the cutting oil is stopped, so that the braking force of the disc brake 21 is reduced. As a result, the rotary casing 12 becomes rotatable. Then, the main shaft 5 is moved in the opposite direction (arrow R).
), The power shaft 4 also rotates in the opposite direction, the driven shaft of the one-way clutch 16 also rotates in the direction of arrow R, and the rotational force in the R direction is applied to the wave generator 17 which is the input shaft of the harmonic drive 20. Is transmitted. As a result, the flexspline 18, which is the output shaft, rotates in the forward direction (the direction of arrow F).

Here, since the rotating casing 12 is fastened to the flexspline 18, the rotating casing 12 rotates in the forward direction (the direction of arrow F) due to the reverse rotation of the main shaft 5, and the tool rotating shaft 8 and the cutting tool 9 are rotated. Is determined. After adjusting the indexing position, the cutting oil is supplied to the disc brake 21 to apply a braking force to the flex spline 18 to stop the rotary casing 12. Since the wave generator 17, the flex spline 18, and the circular spline 19 are always meshed gear trains,
Arbitrary position indexing is possible by rotation of the power shaft 4.

As described above, according to the first embodiment, the indexing position of the cutting tool 9 is adjusted by the rotational force of the main shaft 5 of the machine tool using the one-way clutch 16, so that another driving device is not required. It can be realized at a low cost with a simple structure. Further, since the cutting oil is used as the working fluid, it is not necessary to supply a dedicated working fluid for operating the disc brake 21 from the outside, and thus the structure can be simplified.

FIG. 3 is a side sectional view showing the structure of the angular head 1b according to the second embodiment. A front view schematically showing the vicinity of the tool rotation shaft 8 is the same as FIG. 2, and the same components as those in the first embodiment are denoted by the same reference numerals.

The angular head 1b has a power shaft 4 rotatably mounted on a fixed casing 2 by bearings 3. The power shaft 4 has a tapered connection 4 at its base end.
a, and is fitted coaxially to the main shaft 5 by fitting the tapered connection portion 4a to a tapered connection portion 5a formed at the tip of a main shaft 5 provided in a machine tool such as a machining center.

On the other hand, a detent case 26 is provided at the fixed casing 2 with a knock pin (not shown) at a predetermined set angle.
After being positioned by the like, the bolts (not shown) are used. This is because the angle setting of the detent (generally, the cutting fluid supply bracket 7) with respect to the horizontal line of the main shaft 5 differs depending on the type of machine tool, so that the difference between the types is absorbed. And the case 2 for detent
6 is fixed to a cutting fluid supply bracket 7 provided in the machine tool by a detent pin 6.

A tool rotating shaft 8 is disposed at the end of the power shaft 4 so as to extend in a direction substantially perpendicular to the power shaft 4. The tool rotating shaft 8 has a cutting tool 9 attached to the distal end side and a base end side rotatably attached to a rotating casing 12 by bearings 10 and 11. The bevel gear 13 attached to the tip of the power shaft 4 and the bevel gear 14 inserted into the tool rotation shaft 8 mesh with each other, whereby the rotational force of the main shaft 5 is reduced by the power shaft 4 and the bevel gear 13. , 14 to the tool rotation shaft 8, and the cutting tool 9 rotates.

The rotating shaft 13a of the bevel gear 13 and the power shaft 4 are coaxially connected by a spline structure 27, and the rotating shaft 13a is supported by the rotating casing 12 by a bearing 28. This allows the bevel gear 13 to transmit the rotational force of the power shaft 4 and move in the axial direction of the power shaft 4.

The rotary casing 12 is fixed to the tip of a rod 29a of a hollow cylinder 29 into which the power shaft 4 is inserted. The rod 29a is supported by the bearing 15 and the one-way clutch 16 so as to be rotatable around the power shaft 4 and to be movable in the axial direction. The one-way clutch 16 has a main driving shaft connected to the power shaft 4 and a driven shaft connected to the inner peripheral portion of the rod 29a. The one-way clutch 16 keeps the driven shaft stationary when the power shaft 4 rotates forward (direction of arrow F), and rotates the driven shaft in conjunction with the rotation of the power shaft 4 when rotating reverse (direction of arrow R). Let it. Therefore, the rotational force is transmitted to the rod 29a only when the power shaft 4 reverses.

On the other hand, with respect to the hollow cylinder 29, the base end of the outer cylinder 29b into which the rod 29a is inserted is fixed to the fixed casing 2. The cylinder chamber 30 formed between the outer peripheral portion of the rod 29a and the inner peripheral portion of the outer cylinder 29b is separated from the distal end portion 30a and the proximal end by a brim-shaped partition 31 formed on the outer peripheral portion of the rod 29a. Side part 3
0b. A spring 32 for applying a spring force in the axial direction is housed in the distal portion 30a, while a cutting oil supplied from the cutting fluid supply bracket 7 is supplied to the proximal portion 30b as hydraulic oil. Further, a spring 35 for applying a spring force in the axial direction is wound around a gap 34 between the flange 33 formed at the base end of the rod 29a and the base end of the outer cylinder 29b.

In this structure, the rod 29a is urged toward the base end by the spring force of the springs 32 and 35 when the cutting oil as the hydraulic oil is not supplied to the base end 30b of the cylinder chamber 30. On the other hand, when the cutting oil is supplied, the rod 29a moves to the distal end side against the spring force.

A hearth coupling 36 is fixed to the proximal end face of the flange 33 of the rod 29a.
On the other hand, a hearth coupling 37 is fixed to the fixed casing 2 at a position facing the hearth coupling 36. When the rod 29a is urged toward the proximal end, the teeth 36a and the teeth 37a mesh with each other to
Is stopped around the power shaft 4. On the other hand, rod 29
When a moves to the distal end side, the engagement between the teeth 36a and the teeth 37a is released, and the rod 29a becomes rotatable around the power shaft 4. In the present embodiment, the one-way clutch 1
The structure directly connected to the rotary casing 12 and the hearth couplings 36 and 37 constitute a transmission braking mechanism.

The operation of the angular head 1b having the above configuration at the time of cutting will be described. Turn the spindle 5 in the forward direction (arrow F
), The power shaft 4 and the bevel gear 13 also rotate forward, and accordingly, the bevel gear 14 and the tool rotating shaft 8 rotate in the cutting direction C, and at the same time, the cutting tool 9 also rotates in the cutting direction C. A cutting process can be performed on a work (not shown).

At this time, the one-way clutch 16 does not transmit the rotational force to the rod 29a.
Does not rotate. Further, a force for rotating the rotary casing 12 around the power shaft 4 acts on the rotary casing 12 by a reaction force of the cutting force.
a, the rod 29a engages the teeth 36a of the hearth coupling 36 with the teeth 37a of the hearth coupling 37 fixed to the stationary casing 2, and the stationary casing 2 is Further, since it is fixed to the cutting fluid supply bracket 7 of the machine tool via the detent pin 6, the rotating casing 12 does not rotate.

Next, the operation when the position of the cutting tool 9 is determined will be described. After machining by the cutting tool 9 is completed, when cutting oil is supplied to the base end portion 30b of the cylinder chamber 30 of the hollow cylinder 29, the rod 2 is pressed against the spring force of the springs 32 and 35.
9a and the rotary casing 12 are integrally formed,
And the engagement between the hearth couplings 36 and 37 is released. At this time, the rotating shaft 13a of the bevel gear 13 also moves in the axial direction with the movement of the rotating casing 12 in the axial direction. However, the bevel gear 13
The engagement of the bevel gear 14 does not come off. In this state, the spring 35 disposed on the base end side of the rod 29a is in this state.
, The rotary casing 12 does not rotate by itself even if the engagement between the hearth couplings 36 and 37 is released due to the frictional resistance.

Subsequently, when the main shaft 5 is rotated in the reverse direction (the direction of the arrow R), the one-way clutch 16 functions to transmit the torque to the rod 29a, and the rod 29a rotates in the direction of the arrow R. The casing 12 also rotates at the same time, and the position of the tool rotation shaft 8 and the cutting tool 9 is determined. When the supply of the working fluid (working oil) to the hollow cylinder 29 is stopped after rotating the rotating casing 12 to a desired rotation angle, the rod 29a moves to the proximal end side by the spring force of the springs 32 and 35, and Hearth coupling 3
Positioning is performed by the engagement of 6 and 37.

As described above, according to the second embodiment, the indexing position of the cutting tool 9 is adjusted by the rotational force of the main shaft 5 of the machine tool using the one-way clutch 16, so that another drive device is not required. It can be realized at a low cost with a simple structure. Further, since the cutting oil is used as the working fluid, there is no need to externally supply a dedicated working fluid for operating the hollow cylinder 29, and thus the structure can be simplified.

FIG. 4 is a sectional side view showing the structure of the angular head 1c according to the third embodiment, FIG. 5 is a sectional view taken along the line VV of FIG. 4, and FIG. FIG. 5 is a plan view as viewed from an arrow VI in FIG. 4. The same components as those in the first and second embodiments are denoted by the same reference numerals.

The angular head 1c has a power shaft 4 rotatably mounted on a fixed casing 2 by bearings 3. The power shaft 4 has a tapered connection 4 at its base end.
a, and is fitted coaxially to the main shaft 5 by fitting the tapered connection portion 4a to a tapered connection portion 5a formed at the tip of a main shaft 5 provided in a machine tool such as a machining center.

On the other hand, the non-rotating case 26 is fixed to the fixed casing 2 by a bolt (not shown) after being positioned at a predetermined set angle by the knock pin 26a or the like. This is because the angle setting of the detent (generally, the cutting fluid supply bracket 7) with respect to the horizontal line of the main shaft 5 differs depending on the type of machine tool, so that the difference between the types is absorbed. And the case 26 for detent is
The non-rotating pin 6 is fixed to a cutting fluid supply bracket 7 provided in the machine tool.

A tool rotating shaft 8 is disposed at the end of the power shaft 4 so as to extend in a direction substantially perpendicular to the power shaft 4. The tool rotating shaft 8 has a cutting tool 9 attached to the distal end side and a base end side rotatably attached to a rotating casing 12 by bearings 10 and 11. The bevel gear 13 attached to the tip of the power shaft 4 and the bevel gear 14 inserted into the tool rotation shaft 8 mesh with each other, whereby the rotational force of the main shaft 5 is reduced by the power shaft 4 and the bevel gear 13. , 14 to the tool rotation shaft 8, and the cutting tool 9 rotates.

The rotary casing 12 is held between the power shaft 4 and the fixed casing 2 with the main shaft side (base end side) held by bearings 15 and 40. The holding plate 41 put on,
Since they are held together in the axial direction by 42, they cannot be moved in the axial direction, but can rotate around the power shaft 4 unless the gear trains 43 to 48 described later are engaged.

The power shaft 4 has a one-way clutch 1
6 are connected. This one-way clutch 16
A main drive shaft is connected to the power shaft 4 and a worm gear 43 is fixed to the driven shaft. A worm 44 meshes with the worm gear 43, and the worm 4
A bevel gear 45 is formed at the end of the fourth rotating shaft 44a.

On the other hand, a worm gear 46 is fixed on the outer periphery of the base end of the rotary casing 12 at a position close to the worm gear 43, and a worm 47 meshes with the worm gear 46. A bevel gear 48 is formed at the tip of the rotation shaft 47 a of the worm 47. The rotating shaft 44a of the worm 44 is arranged such that the bevel gear 45 is located on the side of the rotary casing 12, whereby the bevel gear 45 and the bevel gear 48 mesh with each other. The rotating shafts 44a and 47a are supported by the fixed casing 2 respectively.

Since the gear trains 43 to 48 are formed between the one-way clutch 16 and the rotary casing 12, the torque transmitted to the driven shaft of the one-way clutch 16 is transmitted to the worm gear 43, the worm 44, and the Gear 4
5, the bevel gear 48, the worm 47, and the worm gear 48 are transmitted in this order, whereby the rotating casing 12 to which the worm gear 48 is fixed rotates. The one-way clutch 16 keeps the driven shaft stationary when the power shaft 4 rotates forward (direction of arrow F), and rotates the driven shaft in conjunction with the rotation of the power shaft 4 reversely (direction of arrow R). Let it. Therefore, the rotational force is transmitted to the worm gear 43 only when the power shaft 4 reverses. In this embodiment, a transmission braking mechanism is constituted by the gear trains 43 to 48.

The operation at the time of cutting in the angular head 1c having the above configuration will be described. Turn the spindle 5 in the forward direction (arrow F
), The power shaft 4 and the bevel gear 13 also rotate forward, and accordingly, the bevel gear 14 and the tool rotating shaft 8 rotate in the cutting direction C, and at the same time, the cutting tool 9 also rotates in the cutting direction C. A cutting process can be performed on a work (not shown).

At this time, since the one-way clutch 16 does not transmit the rotational force to the worm gear 43, the rotary casing 12 does not rotate. In addition, a force for rotating the rotary casing 12 about the power shaft 4 acts on the rotary casing 12 by a reaction force of the cutting force, and the meshing state between the worm gear 46 and the worm 47 fixed to the rotary casing 12 is so-called. Because of the self-locking state, the rotating casing 12 does not rotate during cutting.

Next, the operation at the time of indexing the position of the cutting tool 9 will be described. When the main shaft 5 is rotated in the reverse direction (the direction of arrow R) after the machining by the cutting tool 9, the power shaft 4 also rotates in the reverse direction, and the driven shaft of the one-way clutch 16 also rotates in the direction of arrow R, and the worm gear The rotational force in the R direction is transmitted to 43. And, as described above, this rotational force
The worm 44, bevel gear 45, bevel gear 48, worm 47, and worm gear 46 are transmitted in this order. As a result, the rotary casing 12 rotates in the direction of arrow R, and the position of the tool rotation shaft 8 and the cutting tool 9 is determined. still,
Since the head gear trains 43 to 48 are always meshing gear trains, any position can be indexed by the rotation of the power shaft 4.

As described above, according to the third embodiment, the indexing position of the cutting tool 9 is adjusted by the rotational force of the main shaft 5 of the machine tool using the one-way clutch 16, so that another driving device is not required. It can be realized at a low cost with a simple structure.

FIG. 7 is a side sectional view showing the structure of an angular head 1d according to a fourth embodiment, and FIG. 8 is an exploded perspective view schematically showing a drive mechanism of the rotary casing 12. It is to be noted that the same reference numerals as those in the first to third embodiments are given.

The angular head 1 c has a power shaft 4 rotatably mounted on a fixed casing 2 by bearings 3. The power shaft 4 has a tapered connection 4 at its base end.
a, and is fitted coaxially to the main shaft 5 by fitting the tapered connection portion 4a to a tapered connection portion 5a formed at the tip of a main shaft 5 provided in a machine tool such as a machining center.

On the other hand, the non-rotating case 26 is fixed to the fixed casing 2 by a bolt (not shown) after being positioned at a predetermined angle by the knock pin 26a or the like. This is because the angle setting of the detent (generally, the cutting fluid supply bracket 7) with respect to the horizontal line of the main shaft 5 differs depending on the type of machine tool, so that the difference between the types is absorbed. And the case 26 for detent is
The non-rotating pin 6 is fixed to a cutting fluid supply bracket 7 provided in the machine tool.

Further, a tool rotating shaft 8 is disposed on the tip side of the power shaft 4 so as to extend in a direction substantially perpendicular to the power shaft 4. The tool rotating shaft 8 has a cutting tool 9 attached to the distal end side and a base end side rotatably attached to a rotating casing 12 by bearings 10 and 11. The bevel gear 13 attached to the tip of the power shaft 4 and the bevel gear 14 inserted into the tool rotation shaft 8 mesh with each other, whereby the rotational force of the main shaft 5 is reduced by the power shaft 4 and the bevel gear 13. , 14 to the tool rotation shaft 8, and the cutting tool 9 rotates.

The rotary casing 12 has a connecting member 51 fixed to the main shaft side (base end side).
1 is held by bearings 52, 52 and attached to the distal end side of the fixed casing 2. Furthermore, the rotating casing 12 is held in the axial direction by holding plates 41 and 42 attached to the tip of the fixed casing 2. Therefore, the rotary casing 12 cannot move in the axial direction, but if not connected to a drive mechanism described later, the power shaft 4
It can rotate around.

Further, a one-way clutch 16 is connected to the power shaft 4. This one-way clutch 16
The main driving shaft is connected to the power shaft 4 and the driven shaft is connected to a rotating member 53. The one-way clutch 16 keeps the driven shaft stationary when the power shaft 4 rotates forward (direction of arrow F), and rotates the driven shaft in conjunction with the rotation of the power shaft 4 reversely (direction of arrow R). Let it. Therefore,
Only when the power shaft 4 rotates in the reverse direction, the rotational force is transmitted to the rotating member 53.

The rotating member 53 has a plurality of (four in this embodiment) insertion holes 53a formed parallel to the axial direction, and a plurality of (four in this embodiment) holes on the outer peripheral portion.
Is provided. The insertion holes 53a are formed at equal intervals on the same circumference. The pins 53b are also formed at equal intervals on the same circumference. The rotating member 53 is mounted rotatably around the power shaft 4 by the one-way clutch 16 and the bearing 15. One end of a helical spring 54 wound around the power shaft 4 is fixed to the rotating member 53, and the other end of the helical spring 54 is fixed to the fixed casing 2.

A substantially annular joint member 55 is mounted on the outer side in the circumferential direction of the rotating member 53. The joint member 55 is
Four cam grooves 56 are formed in the inner peripheral portion. Cam groove 5
Reference numeral 6 denotes a pin to which the pin 53b of the rotating member 53 is engaged, and a parallel portion 56a extending along the axial direction from the front end side toward the main shaft, and a parallel portion 56a inclined from the parallel portion 56a toward the main shaft. And an inclined portion 56b extending therefrom. And
By engaging the cam groove 56 with the pin 53b,
The joint member 55 is mounted on the rotating member 53. Also, the joint member 55 has teeth 55a on the outer peripheral portion, and by meshing the teeth 55a with the teeth 57 formed on the inner peripheral portion of the fixed casing 2, the joint member 55 does not rotate but can slide in the axial direction. To the fixed casing 2.

Further, the joint member 55 is urged to the distal end by a spring 58 attached to the fixed casing 2, and the teeth 55 b formed on the distal end surface are connected to the connecting member 5.
1 is meshed with the teeth 51a formed on the proximal end surface. Therefore, in this state, the rotation of the rotary casing 12 is stopped. The teeth 55b and 51a correspond to the hearth coupling teeth.

Further, another rotating member 59 is mounted on the rotating member 53. The rotating member 59 is shown in FIG.
As shown in FIG. 5, a plurality of small-diameter portions 59a and a large-diameter portion 59b are formed in a substantially annular shape, and a plurality of small-diameter portions 59a extend in the axial direction (in the present embodiment, four
Book) rod 60 is attached. And rod 6
The rotation member 59 is attached to the rotation member 53 by letting 0 pass through the insertion hole 53 a of the rotation member 53. Further, a spring 61 is mounted on each rod 60, one end of the spring 61 is fixed to the rod 60, and the other end is
3 is fixed to the front end surface. Therefore, the rotating member 5
9 is urged toward the distal end by the spring force of the spring 61, and the small-diameter portion 59 a is in contact with the end surface on the main shaft side of the rotating member 53.

The outer diameter of the large-diameter portion 59b is
Are formed so as to be larger than the outer diameter of the joint member 55, and the outer peripheral surface of the large diameter portion 59b can be brought into contact with the main shaft side end surface of the joint member 55.

A substantially annular joint member 62 is attached to the tip of the rod 60. The joint member 62 has teeth 6 corresponding to a hearth coupling on the outer peripheral side of the main shaft side end face.
2a. The teeth 62a are connected to the teeth 6 of the joint portion 63a formed on the inner periphery of the coupling member 51 on the main shaft side.
3a. Therefore, when the teeth 51a and 55b mesh with each other and the teeth 62a and 63a do not mesh with each other, the rotary casing 12 does not rotate. In the present embodiment, the structure for directly connecting the one-way clutch 16 to the rotary casing 12, the teeth 51a of the connecting member 51, and the teeth 55b of the joint member 55 constitute a transmission braking mechanism.

The operation at the time of cutting in the angular head 1d having the above configuration will be described. Turn the spindle 5 in the forward direction (arrow F
), The power shaft 4 and the bevel gear 13 also rotate forward, and accordingly, the bevel gear 14 and the tool rotating shaft 8 rotate in the cutting direction C, and at the same time, the cutting tool 9 also rotates in the cutting direction C. A cutting process can be performed on a work (not shown).

At this time, since the one-way clutch 16 does not transmit the rotating force to the rotating member 53, the rotating casing 12
Does not rotate. In addition, a force for rotating the rotary casing 12 about the power shaft 4 acts on the rotary casing 12 by a reaction force of the cutting force, but the spring force of the spring 58 causes the teeth 51 a of the connecting member 51 fixed to the rotary casing 12 to rotate. The teeth 55b of the joint member 55 are meshed with the teeth 55a of the outer peripheral portion of the joint member 55 and the teeth 57 of the inner peripheral portion of the fixed casing 2 are meshed with each other.
Is fixed to the cutting fluid supply bracket 7 by the detent case 26 and the detent pin 6, so that the rotary casing 12 does not rotate.

Next, the operation at the time of indexing the position of the cutting tool 9 will be described. When the main shaft 5 is rotated in the opposite direction (the direction of arrow R) after the machining by the cutting tool 9, the power shaft 4 is also rotated in the opposite direction, and the driven shaft of the one-way clutch 16 is also rotated in the direction of arrow R, thereby turning. The rotational force in the R direction is transmitted to the member 53. Thus, the rod 60 penetrating the rotating member 53 and the rotating member 5 fixed to the rod 60
9 and the joint member 62 also rotate in the R direction. At this time, the helical spring 54 is twisted.

When the rotating member 53 rotates, the pin 53b on the outer periphery of the rotating member 53 moves along the cam groove 56 on the inner periphery of the joint member 55. The cam groove 56 is the pin 53
When b rotates (moves) in the R direction, the joint member 55 is formed so as to move to the right side (spindle side) on the paper surface. Is slid in the axial direction, and the engagement between the joint member 55 and the connecting member 51 is released.

When the joint member 55 moves a predetermined length in the right direction, the joint member 55 is pushed by the end face on the main shaft side and is turned.
Moves in the axial direction (right direction), and the joint member 62 fixed to the rod 60 also moves rightward while pressing the spring 61, whereby the teeth 62a and 63a mesh with each other. When the coupling member 51 and the coupling member 62 are in mesh with each other, the coupling between the coupling member 55 and the coupling member 51 is in a disengaged state. Therefore, when the main shaft 5 (the power shaft 4) is further rotated in the R direction, the coupling member Together with 51, the rotating casing 12 rotates. In this way, the positions of the tool rotation shaft 8 and the cutting tool 9 are determined.

When the main shaft 5 is rotated in the forward direction (the direction of arrow F) after the end of the position indexing, the rotational force from the one-way clutch 16 is not transmitted. Rotate forward. As a result, the pin 53b moves the cam groove 56 in the opposite direction,
In addition, the joint member 55 moves to the left (front end side) by the spring force of the spring 58, and accordingly, the rotating member 59, the rod 60, and the joint member 62 also move to the left, and the joint member 6
2 is disengaged from the connecting member 51, and then the connecting member 5 is disengaged.
1 and the joint member 55 mesh with each other, whereby the rotary casing 12 is positioned.

As described above, according to the fourth embodiment, the indexing position of the cutting tool 9 is adjusted by the rotational force of the main shaft 5 of the machine tool using the one-way clutch 16, so that another driving device is not required. It can be realized at a low cost with a simple structure.

FIG. 9 is a side sectional view showing a structure of an angular head 1e according to a fifth embodiment, and FIG. 10 is a perspective view of indexing disks 72 and 73 provided in the angular head 1e. In addition, the front view which shows the outline of the vicinity of the tool rotation shaft 8 is:
It is the same as FIG. 2, and the same components as those in the first to fourth embodiments are denoted by the same reference numerals.

The angular head 1 c has a power shaft 4 rotatably mounted on a fixed casing 2 by a bearing 3. The power shaft 4 has a tapered connection 4 at its base end.
a, and is fitted coaxially to the main shaft 5 by fitting the tapered connection portion 4a to a tapered connection portion 5a formed at the tip of a main shaft 5 provided in a machine tool such as a machining center.

On the other hand, the non-rotating case 26 is fixed to the fixed casing 2 by a bolt (not shown) after being positioned at a predetermined set angle by the knock pin 26a or the like. This is because the angle setting of the detent (generally, the cutting fluid supply bracket 7) with respect to the horizontal line of the main shaft 5 differs depending on the type of machine tool, so that the difference between the types is absorbed. And the case 26 for detent is
The non-rotating pin 6 is fixed to a cutting fluid supply bracket 7 provided in the machine tool.

Further, a tool rotating shaft 8 is disposed on the distal end side of the power shaft 4 so as to extend in a direction substantially perpendicular to the power shaft 4. The tool rotating shaft 8 has a cutting tool 9 attached to the distal end side and a base end side rotatably attached to a rotating casing 12 by bearings 10 and 11. The bevel gear 13 attached to the tip of the power shaft 4 and the bevel gear 14 inserted into the tool rotation shaft 8 mesh with each other, whereby the rotational force of the main shaft 5 is reduced by the power shaft 4 and the bevel gear 13. , 14 to the tool rotation shaft 8, and the cutting tool 9 rotates.

The rotary casing 12 is rotatably mounted on the power shaft 4 by a pair of bearings 15, 15 and a one-way clutch 16 with a connecting portion 70 formed on the base end side. The connecting portion 70 is housed on the distal end side of the fixed casing 2 in a state where the bush 71 is inserted into the outer peripheral portion. Furthermore, the rotating casing 12 is held in the axial direction by holding plates 41 and 42 attached to the tip of the fixed casing 2. Therefore, the rotary casing 12 cannot move in the axial direction, but can rotate around the power shaft 4 unless indexing disks 72 and 73 described later are connected.

The one-way clutch 16 is connected to the power shaft 4
When the motor rotates forward (in the direction of arrow F), the driven shaft is kept stationary, while when the power shaft 4 rotates in the reverse direction (in the direction of arrow R), the driven shaft is rotated in conjunction therewith. Therefore, the rotational force is transmitted to the rotary casing 12 only when the power shaft 4 rotates in the reverse direction.

The positioning of the rotary casing 12 is realized by a pair of index disks 72, 73. One indexing disk 72 has an insertion hole through which the power shaft 4 is inserted at the center, and is fixed to the base end surface of the connecting portion 70 of the rotary casing 12 by bolting or the like. The other indexing disk 73 also has an insertion hole for inserting the power shaft 4 at the center similarly, and the outer peripheral portion is connected to the inner peripheral portion of the fixed casing 2 by a spline structure. Is movable. The indexing disk 73 is urged toward the distal end by springs 74, 74 provided on the fixed casing 2, and the indexing disk 72 disposed opposite thereto.
It is in a state of being engaged. Therefore, in this state, the rotary casing 12 does not rotate.

By the way, each of the indexing disks 72 and 73 has a plurality of (four in FIG. 10) convex portions 7 on the outer peripheral side of the surface.
This is a so-called face cam disk having 5... 75 and 76. The convex portions 75 and 76 have gentle inclination surfaces 75a and 76a having a small angle and steep inclination surfaces 75b and 76b having a large angle with respect to a plane perpendicular to the axis. However, the index disks 72 and 73 are set so that the positional relationship of the inclined surfaces is reversed. That is, when the top of the convex portion is used as a reference, the indexing disk 72 rotates the power shaft 4 forward (arrow F).
Direction) side is a steeply inclined surface 75b, and reverse rotation (arrow R direction)
The side is a gentle inclined surface 75a. On the other hand, in the indexing disk 73,
The forward rotation side is a gentle slope 76a, and the reverse rotation side is a steep slope 76a.
b. As a result, the convex portions of one indexing disk fit into the recesses (between the two convex portions) of the other indexing disk facing each other, and the indexing disks 72 and 73 mesh with each other. Further, by setting the inclined surface as described above, the indexing disk 73 on the fixed casing 2 side is fixed, and the rotating casing 12 is fixed.
When rotating the indexing disk 72 on the side, it is easier to rotate when rotating in the reverse direction than in rotating forward. This is because, in the case of forward rotation, the convex portion 75 of the indexing disk 72 must climb over the steeply inclined surface 76b, whereas in the case of reverse rotation, the gently inclined surface 76b.
This is because it is only necessary to get over a.

Incidentally, the convex portions 75 of the indexing disks 72, 73,
The number 76 is determined based on the number of index positions. For example, in the case of 90 ° indexing, at least four are required as shown in FIG. 10, and in the case of 180 ° indexing, at least two are required. In the present embodiment, the structure for directly connecting the one-way clutch 16 to the rotary casing 12 and the indexing disks 72 and 73 constitute a transmission braking mechanism.

The operation at the time of cutting in the angular head 1e having the above configuration will be described. Turn the spindle 5 in the forward direction (arrow F
), The power shaft 4 and the bevel gear 13 also rotate forward, and accordingly, the bevel gear 14 and the tool rotating shaft 8 rotate in the cutting direction C, and at the same time, the cutting tool 9 also rotates in the cutting direction C. A cutting process can be performed on a work (not shown).

At this time, since the one-way clutch 16 does not transmit a rotational force to the connecting portion 70 of the rotary casing 12, the rotary casing 12 does not rotate. Also,
A force for rotating the rotary casing 12 around the power shaft 4 acts on the rotary casing 12 by the reaction force of the cutting force. The indexing disk 72 fixed to the connecting portion 70 of the rotary casing 12
And the indexing disk 73 fixed to the fixed casing 2 are engaged with each other. Further, since the fixed casing 2 is fixed to the cutting fluid supply bracket 7 by the detent case 26 and the detent pin 6, the rotating casing 12 does not rotate.

Next, the operation at the time of indexing the position of the cutting tool 9 will be described. When the main shaft 5 is rotated in the opposite direction (the direction of arrow R) after the machining by the cutting tool 9, the power shaft 4 is also rotated in the opposite direction, and the driven shaft of the one-way clutch 16 is also rotated in the direction of arrow R. Rotational force in the R direction is transmitted to 12. As a result, the indexing disk 72 rotates along the gentle inclined surface 76a of the indexing disk 73, and the indexing disk 73 presses and compresses the spring 74 to move to the main shaft side (to the right in the figure), thereby performing indexing. When the convex portion 75 of the disk 72 gets over one convex portion 76 of the indexing disk 73, it returns to its original position by spring force and meshes with the indexing disk 72 again. Therefore, the tool rotation shaft 8 is rotated by 90 °. In this way, the positions of the tool rotation shaft 8 and the cutting tool 9 are determined.

As described above, according to the fifth embodiment, the indexing position of the cutting tool 9 is adjusted by the rotational force of the main shaft 5 of the machine tool using the one-way clutch 16, so that another driving device is not required. It can be realized at a low cost with a simple structure.

[Brief description of the drawings]

FIG. 1 is a side sectional view showing a first embodiment.

FIG. 2 is a schematic front view of the vicinity of a tool rotation axis according to the first embodiment.

FIG. 3 is a side sectional view showing a second embodiment.

FIG. 4 is a side sectional view showing a third embodiment.

FIG. 5 is a cross-sectional view taken along the line VV of FIG. 4;

FIG. 6 is a plan view seen from the direction of arrow VI in FIG. 4;

FIG. 7 is a side sectional view showing a fourth embodiment.

FIG. 8 is an exploded perspective view of a drive mechanism provided in a fourth embodiment.

FIG. 9 is a side sectional view showing a fifth embodiment.

FIG. 10 is a perspective view of an indexing disk included in a fifth embodiment.

[Explanation of symbols]

 1a Angular head 2 Fixed casing 4 Power shaft 5 Main shaft 8 Tool rotating shaft 9 Cutting tool 12 Rotating casing 13 Bevel gear 14 Bevel gear 16 One-way clutch 17 Wave generator 18 Flex spline 19 Circular spline 20 Harmonic drive 21 Disk brake

Claims (2)

[Claims] 1. A power shaft (4) coaxially mounted on a main shaft (5) of a machine tool that can be driven forward and reverse, and a cutting tool arranged in a direction intersecting the power shaft (4). A tool rotating shaft (8) to which (9) is attached; and the power shaft (4) as power in the cutting direction on the tool rotating shaft (8).
Power transmission mechanism (13) (14) for transmitting forward rotation force from motor
A rotary casing (12) that supports the tool rotation shaft (8) and is rotatable around the power shaft (4); and a main drive shaft is connected to the power shaft (4). A one-way clutch (16) for rotating the driven shaft when the power shaft (4) rotates reversely while the driven shaft is stationary when the power shaft (4) rotates forward, and the one-way clutch (16). When the driven shaft is stationary, the rotation of the rotary casing (12) is stopped, while when the driven shaft rotates, the rotary casing (12) is stopped.
And a transmission braking mechanism (20) (21) for rotating the angular head in conjunction therewith. 2. The transmission braking mechanism according to claim 1, wherein the rotation of the rotary casing (12) is stopped by using a braking means (21) that operates with a cutting fluid supplied to the cutting tool (9) as a working fluid. 3. The angular indexable head according to claim 1, wherein: