KR100436249B1 - apparatus of turret-head - Google Patents

Abstract

The present invention relates to a turret head device installed in a machine tool to selectively drive the turret and the rotary tool with a single drive motor. The present invention installs a drive motor 101 on the rear of the frame 10 and selectively drives the operation of the rotary tool 120 and the automatic tool exchange due to indexing the disk 119 by the power of the drive motor 101. In the turret head device, the first outer tooth spur gear 103 and the edge of the first outer tooth spur gear 103 are formed on the edge circumferential side of the motor shaft 102 by receiving rotational power from the driving motor 101. A spur gear 105 engaged with a circumferential side surface to form a spline portion therein, a cylinder portion 104 positioned at an outer circumference of the spur gear 105, and a spline spur when the cylinder portion 104 is hydraulically reversed Swivel Cubic Coupling 108 engaged with Gear 106 and interlocked, Ring Gear 109 interdigitated with Spline Gears 106 during forward operation of cylinder portion 104, and Swivel Cubic Couple It is formed on the inner surface of the ring 108 and the ring gear 109 and the frame ( 10) and a fixed cubic coupling 111 that is bolted integrally with the teeth, and teeth are formed on the opposite side of the teeth of the swinging cubic coupling 108 and the fixed cubic coupling 111 to advance by the inflow and outflow of hydraulic pressure. Alternatively, the piston cubic coupling 110 is coupled to or spaced apart from the backward, and the piston cubic coupling 110 and the fixed cubic coupling 111 and the frame 10 which are sequentially coupled are formed at the center of the inner surface of the frame 10. The second shaft 112 for supporting the disk 119 rotational motion of the front surface with the needle bearing 135, and is installed on the side of the housing 10 and in conjunction with the ring gear 109 to the rotary tool 120 It includes a small gear 114 for transmitting the rotational power. Accordingly, the same drive motor can be used to selectively change the automatic tool change and power transmission of the rotating tool, simplify the control by reducing the number of parts, and simultaneously operate the oil by one inflow and outflow of the tool. Reduce the time for exchange In addition, it is possible to minimize the volume of the housing by reducing the number of parts installed in the housing, and there is an effect that can be used in the standard tool set of the turret lathe and turn mill vertical lathe tool bar.

Description

Turret head unit {apparatus of turret-head}

The present invention relates to a turret head device for a machine tool, and more particularly, to a turret head device installed in a machine tool to selectively drive the turret and the rotary tool with a single drive motor.

Generally, a turret head device installed in a Numerically Controlled Lathe or a Machining Center (MC) is a driving motor. A tool required by a user rotates the turret to be positioned on the top or side of a workpiece. The selected tool located on the top or side of the workpiece drives another auxiliary motor mounted on the top or side, and the driven auxiliary motor rotates the tool to perform hole processing or cutting on the workpiece.

However, in recent years, the turret head device has been developed such that the rotation of the turret and the rotation of the tool are simultaneously performed by one main motor instead of a plurality of motors. An example is the prior art European Patent Publication No. EP 0 765 499 B1.

The European Patent Publication No. EP 0 765 499 B1 has a configuration in which the turret head device for the tool bar has a cylindrical housing 10 and a motor 15 at the rear of the housing 10, as shown in FIG. 4. ) Is attached. The first and second interlocking gear parts 20 and 30 are enclosed in the housing 10, and the tool drive shaft 51 is enclosed in the turret 40.

The first and second interlocking gear parts 20 and 30, the motor 15, and the turret 40 are lined up along with the central axis of the housing 10. The housing 10 is formed on the front of the relatively large diameter body portion 11, the rear member 13 is coupled to the end of the body portion (11). In addition, the auxiliary member 14 is accommodated in the body portion 11 in addition to the rear of the front member (12). The motor 15 is formed on the rear surface of the rear member 13.

The first and second interlocking gear parts 20 and 30 are formed by positioning the sun gears 21 and 31 at the center thereof, respectively, and the carriers 23 and 33 are formed on the spur gears 22 and 32, respectively. The ring gears 24 and 34 are internally driven with the spur gears 22 and 32 to drive. A plurality of spur gears 22 and 32 are provided on the same circumferential carriage 23 and 33.

The ring gear 24 of the first interlocking gear part 20 is formed on the inner rear surface of the carrier 33 of the second interlocking gear part 30, and the sun gear 31 of the second interlocking gear part 30 is formed. It is formed to protrude on the front surface of the carrier 23 formed in the first interlocking gear portion 20.

The sun gear 21 of the first interlocking gear portion 20 is enclosed to rotate between the bearings and in the carriage 23. The spool line 21a is formed by being attached to the rear surface of the sun gear 21, and the cylindrical member 25 is formed by being attached to the rear surface of the carriage 23.

The support member 35 is connected to the rear end of the carriage 33 of the second interlocking gear portion 30. The carriage 33 and the support member 35 pass through the metal bushes 36a and 36b which are rotatable for friction prevention purposes, and are enclosed in the front member 12 and the body portion 11 of the housing, and the front and rear surfaces thereof. It is formed to allow movement.

Another support member 34a is coupled to the rear surface of the ring gear 34, and the ring gear 34 passes through the support member 34a and a bearing so as to be rotatable at the outer rear of the carriage 33. Formed. The bearing is fixed by a nut.

The drive member 37 is arranged on the outer surface of the support member 35 connected with the carriage 33. The driving member 37 is coupled to the supporting member 35 through the joint beam and the nut, together with the pressure member 37a having a relatively large diameter, which is open toward the front portion of the supporting member 35.

The ring member 14a is formed at the rear end of the auxiliary member 14 formed in the housing 10. In addition, at the highest point of the diameter of the driving member 37, the hydraulic chamber 14b divided into the front and rear surfaces is inserted between the ring member 14a and the auxiliary member 14. The outer surface of the drive member 37 has two points in contact with the auxiliary member 14.

The hydraulic chamber 14b is connected to a hydraulic oil source located outside the housing 10 with the rear oil path and the front surface independent from each other.

The driving member 37 is operated by the inflow and outflow of the hydraulic pressure to move the front or rear of the hydraulic chamber 14b through the oil path in the support member 35 and the carriage 33, and the driving member 37 By the front and rear operation.

When the carriage 33 is turned to the front, the pressure member 37 applies a predetermined pressure to the clutch 38, and rotates the ring gear 34 to the clutch 38 through the support member 34a. Make it possible. When the carriage 33 moves to the rear side, the ring gear 34 and the support member 34a are released.

The turret 40 is connected with the front end of the carriage 33. The combined gear parts 41 and 16 are formed on the front surface of the entire member 12 of the housing 10. The gears 41 and 16 may be spaced apart by the retraction when the turret 40 operates through the carriage 33.

Accordingly, the operation of the turret 40 is possible by connecting the ring gear 34 of the second interlocking gear part 30 to the clutch 38 that controls the joining or loosening.

The auxiliary shaft 52 is formed on the front surface of the carriage 33 through the angular contact bearing to rotate. The auxiliary shaft 52 is connected to the sun gear 31 of the second interlocking gear part 30. In addition, the auxiliary shaft 52 is connected to the carriage 23 of the first interlocking gear portion 20. And bevel gears (52a, 52d) connected to the front end of the carrier material 33 is connected.

The tool drive shaft 51 is rotatably formed in the turret 40 through the bearing. The tool drive shaft 51 is sequentially connected to the carriage 23 of the first interlocking gear part 20 through the sun gear 31, the auxiliary shaft 52, and the bevel gears 52a and 52d.

However, since the spool line and the bevel gear, which are elongated, must be installed inside the housing, the inertia force generated when the turret rotates due to the rotation of the turret drive shaft is increased due to the increase in the volume of the housing or the increase in weight. There is a problem that the time is long.

In addition, since the number of parts installed inside the housing is large, it is difficult to reposition and repair the parts in the event of wear of gears or breakdown of the hydraulic circuit, and the volume of the housing increases further for use in turn mill vertical lathes. There is a big problem in the common use in the tool bar and turn mill vertical tool bar of the lathe.

The present invention has been made to solve the above problems, it is possible to selectively drive the rotation of the turret head and the rotation of the rotary tool with a single drive motor, the time of the index by reducing the inertial force when the turret rotates It is an object of the present invention to provide a turret head device for a machine tool which shortens and reduces the number of parts to be installed to minimize the volume of the housing.

According to the present invention, the drive motor 101 is installed on the rear of the frame 10 and the automatic tool exchange and operation of the rotary tool 120 due to indexing the disk 119 by the power of the drive motor 101. In the turret head device for selectively driving the first outer tooth spur gear 103 and the first outer tooth spur gear 103 formed on the edge circumferential side of the motor shaft 102 receives the rotational power from the drive motor 101 The spur gear 105 is engaged with the edge circumferential side of the 103 to form a spline therein, the cylinder portion 104 located at the outer circumference of the spur gear 105, and the cylinder portion 104 is hydraulically applied. A turning cubic coupling 108 engaged with and interlocked with the spline spur gear 106 during the reverse operation, and a ring gear 109 interdigitated with and interlocked with the spline per gear 106 during the forward operation of the cylinder portion 104; Internal surfaces of the pivotal coupling 108 and the ring gear 109. And a tooth formed on a side opposite to the teeth of the pivotal coupling 108 and the fixed curb coupling 111, which are formed and bolted integrally with the frame 10. Piston Cubic Coupling (110) which is coupled or spaced forward or backward by the outflow, and the piston Cubic Coupling (110), fixed Cubic Coupling (111) and the inner surface of the frame (10) which are sequentially coupled And a second shaft 112 for supporting the disk 119 rotational motion of the front surface of the frame 10 with the needle bearing 135 and a rotating tool installed on the side of the housing 10 and interlocked with the ring gear 109. It is achieved by a small gear 114 that transmits rotational power to the (120).

In addition, the cylinder portion 104 is formed on the inside of the spur gear 105 and a spur gear 105 having a predetermined tooth on the rear side of the outer edge and forming a hollow portion 105a on the inner surface thereof and constrained to the side surface. And the spline spur gear 106 for driving forward or backward and coupled to the rear surface of the spline spur gear 106, and interlocked with the piston curb coupling 110 at the same time by the inflow and outflow of hydraulic pressure, the piston curb coupler It is further preferred to further include a piston 107 that moves forward or backward in the opposite direction to the ring 110.

In addition, the cylinder portion 104 preferably further includes forming a hydraulic chamber c (125) and a hydraulic chamber d (126), respectively, on the rear surface of the frame (10).

In addition, the piston cubic coupling 110 is engaged with the fixed cubic coupling 111 and the turning cubic coupling 108 when backing by hydraulic pressure to prevent the flow during the stop operation of the turret head, spline spur It is preferable to further include reducing the operation time by simultaneously performing the gear shifting operation of the gear 106.

In addition, it is preferable to further include forming the hydraulic chamber a (123) and the hydraulic chamber b (124), respectively, the space for the outflow and inflow of the hydraulic pressure on the front and rear of the piston civic coupling (110).

Figure 1a is a cross-sectional view of the automatic tool change operation of the turret head apparatus according to the present invention,

Figure 1b is a sectional view of the rotary tool operation of the turret head apparatus according to the present invention,

Figure 2 is an exploded perspective view of the cylinder portion of the turret head device according to the present invention,

3 is a cross-sectional view of the signal unit and the gear unit of the turret head device according to the present invention;

4 is a cross-sectional view of the turret head apparatus according to the prior art.

Explanation of symbols on main parts of drawing

10; Frame 99; V-ring

101; Drive motor 102; Motor shaft

103; First outer tooth spur gear 104; Cylinder

105; Spur gear 105a; Hollow part

105b; Guide 106; Spline spur gear

106a; Protrusion 107; piston

107a; Retainer 108; Swivel Cirque Coupling

109; Ring gear 110; Piston Cubic Coupling

111; Fixed cubic coupling 112; Second shaft

113; Nameplate 114; Small gear

115; Third gear shaft 116; Hydraulic injection part

117; Hydraulic inlet: 118; Hydraulic inlet b

119; Disk 120; Rotary tools

121; Needle bearing 122; Contact member

123; Hydraulic chamber a 124; Hydraulic chamber b

125; Hydraulic chamber c 126; Hydraulic chamber d

127; Bearing 128; Assembly switch a

129; Assembly switch b 130; Assembly switch c

131; Dog 132; Bracket

133; Bearing 134; flange

135; Needle Bearing

Hereinafter, a turret head device for a machine tool according to the present invention will be described in detail with reference to the accompanying drawings.

Figure 1a is a cross-sectional view of the automatic tool change operation of the turret head device according to the present invention, Figure 1b is a cross-sectional view of the rotary tool operation of the turret head device according to the present invention, Figure 2 is an exploded perspective view of the cylinder portion of the turret head device according to the present invention 3 is a cross-sectional view of a signal unit and a gear unit of the turret head device according to the present invention.

First, the internal configuration of the turret head device for the machine tool is composed of the respective gears and the hydraulic circuit inside the housing as a whole, as shown in Figure 1a, 1b. A drive motor 101 is installed on the rear surface of the frame 10, and a motor shaft 102 for transmitting rotational power is formed in the drive motor 101.

In addition, as shown in Figure 3, the side of the motor shaft 102, the dog 131 formed in a horizontal shape to the upper side is formed, the assembly switch fixed to the bracket 132 on the side of the motor shaft 102 b, c (129, 130) are formed. The assembly switches 129 and 130 serve to detect a rotation operation.

In addition, a first outer tooth spur gear 103 is installed on the outer edge surface of the motor shafter 102 as a peripheral edge surface, and the first outer tooth spur gear 103 is firmly fixed by a plurality of bolts. The plurality of bolts serve to prevent the motor motor 102 from being spaced apart when the RPM of the driving motor 101 increases or rapidly rotates.

On the other hand, the first outer tooth spur gear 103 meshes with the spur gear 105 supported by the bearing 133 on the rear surface of the frame 10, the cylinder portion 104 provided on the outer peripheral portion of the spur gear 105 is As shown in FIG. 2, the spur gear 105, the spline gear gear 106, the piston 107, the retainer 107a, and the bearing 127 are formed as a whole.

The inner surface of the spur gear 105 forms a hollow portion 105a. The hollow portion 105a forms a plurality of elongated guides 105b on the side.

The spline spur gear 106 is inserted into the inner surface of the hollow portion 105a, and the spline spur gear 106 has the same number of rod shapes as the guide 105b of the hollow portion 105a on its rear outer peripheral surface. To form a protrusion 106a. The protrusion 106a is inserted into the guide 105b so as to move forward or backward.

The spline spur gear 106 has a spur gear tooth on its front surface, and is formed in a circular shape so that a circular groove 106b is three-dimensionally formed at predetermined intervals. In addition, a bearing 127 is inserted into the spline spur gear 106 to support and connect the piston 107 with a bolt.

The piston 107 is located at the rear end of the spline gear (106), the hydraulic chamber (123, 126) formed in the front and rear surfaces of the cylinder portion 104 is to be moved forward or backward by the influence of the fluid.

An oil ring and a steel retainer 107a are inserted into the rear end of the cylinder part 106 so that the fluid does not invade the front.

As shown in FIGS. 1A and 1B, the spline spur gear 106 installed on the front surface of the cylinder part 104 is provided with a pivotal coupling 108 and a ring gear 109 vertically formed on the side surfaces thereof. In addition, the assembly switch a (128) for detecting the forward and backward motion is located on the upper side of the spline spur gear 106.

The pivotal cubic coupling 108 has a spur gear type on the side of the edge and forms another crown gear type on the front side. The spur gear type formed on the edge side is to be engaged with the spline spur gear 106, the crown gear type is to be engaged with the piston cubic coupling 110 formed on the front surface.

The ring gear 109 has the same diameter as the gear formed on the outer circumference of the turning cubic coupling 108 installed in the frame 10, has a spur gear type on its edge and has a plurality of needle bearings in the center ( 135 is inserted into the outer peripheral surface of the flange 134 to be rotatable.

The inside of the turning cubic coupling 108 is formed with a fixed cubic coupling 111 fixed to the frame 10 by a bolt 12. The fixed cubic coupling 111 is configured to be spaced apart from the piston pivotal coupling 108, the tooth is formed toward the disk 119. The tooth of the fixed cubic coupling 111 is formed in the same direction as the crown gear type of the turning cubic coupling 108 to be engaged with the piston cubic coupling 110. In addition, the fixed cubic coupling 111 is coupled to the frame 10 by a bolt 12 is fixed firmly.

The piston cubic coupling 110 is to be able to move forward and backward by hydraulic pressure, the teeth face the crown gear type and the tooth of the fixed cubic coupling (111) of the piston turning civic coupling (108). In this case, the piston cubic coupling 110 is engaged when the reverse.

In addition, the frame 10 prevents the fixed cubic coupling 111 from being pushed to the rear side any more when the piston cubic coupling 110 is reversed, and the piston curvic coupling 110 and the second shaft 112. In addition, the hydraulic chambers 124 and 125 are formed to contact the fluid when the hydraulic pressure flows in or out, and is formed in contact with the fixed cubic coupling 111.

The frame 10, the fixed cubic coupling 111 and the turning cubic coupling 108, the contact member 122, and the piston cubic coupling 110 are sequentially formed in order of being close to the driving motor 101. The second shaft 112 is formed therein. The second shaft 112 provides a hydraulic movement passage, supports the disk 119 exposed to the outside of the frame 10 on the front surface with the needle bearing 121 so as to rotate without friction, and constitutes a cutting flow passage. It has a plate 113.

The disk 119 and the rotary tool 120 is disposed in front of the frame 10. The rotary tool 120 enables milling or boring operations. In addition, a v-ring 99 such as rubber packing is inserted to prevent leakage of fluid due to hydraulic pressure during operation between the gears inside the frame 10.

The operation of the turret head device for the machine tool is shown in Figs. 1A and 1B. As a whole, when the predetermined hydraulic pressure is input to the hydraulic inlets 117 and 118, the respective gears are engaged with each other.

As shown in Figure 1a, when the hydraulic pressure is injected into the hydraulic inlet a (117) through a hydraulic controller (not shown) located outside the frame 10, the operation is as follows.

First, the hydraulic pressure is introduced into the hydraulic inlet a (117), and the hydraulic pressure is introduced into the hydraulic chamber b (124). As the hydraulic pressure flows into the hydraulic chamber b 124, the piston curb coupling 110 moves forward.

At the same time, the hydraulic pressure flows into the hydraulic chamber c 125 through the flow path formed in the frame 10 and the cylinder portion 104, and the piston 107 moves backward by the inflow of the hydraulic pressure. The spline spur gear 106 fixed to the piston 107 by the bearing 127 is moved to be fastened to the turning cubic coupling 108 so that automatic tool exchange is possible.

At the same time, the hydraulic chamber c (125) has a narrower cross-sectional area than the hydraulic chamber (b 124) into which the hydraulic pressure flows, so that gear shifting is performed accurately.

As shown in FIG. 3, the operation check dog 131 in which the spline spur gear 106 is meshed with a gear formed on the outer surface of the turning cubic coupling 108 is moved forward and backward by hydraulic pressure. Is fastened and coupled to the screw (137) to (110), the dog 131 is formed horizontally toward the rear of the piston cubic coupling 110. In addition, a bracket 132 is fixed to the rear of the second shaft 112, and proximity switches b and c 129 and 130 having the same specification are vertically positioned on the bracket 132.

The operation of the piston cubic coupling 110 and the spline spur gear 106 is sensed by the proximity switch a 128 and the proximity switch b 129 to perform the operation of the automatic tool change.

First, the rotational force transmitted from the driving motor 10 through the motor shaft 102 is applied to the first outer tooth spur gear 103, and the first outer tooth spur gear 103 is a spur gear 105 of the cylinder part 104. Transmit torque to the The spur gear 105 supported by the bearing 133 of the frame 10 receives the rotational force of the first outer tooth spur gear 103 directly and transmits the rotational force to the spline spur gear 106.

The spline spur gear 106 meshes with the turning cubic coupling 108 located at the side of the spline piston 107 coupled to the rear while being reversed by hydraulic pressure. The spline spur gear 106 having the rotational force transmits the rotational power to the spur gear type formed on the edge side of the turning cubic coupling 108, and the turning curvature coupling 108 is driven by the transmitted rotational force. .

The pivotal cubic coupling 108 is coupled with a bolt 50 fastened to the disk 119 and the screw groove 52 located on the front, so that the disk 119 also interlocks when rotating. The entire interlocked disk 119 rotates around the second shaft 112, and indexes the position of the rotary tool 120 attached to the front surface of the disk 119. At this time, the small gear 114 and the ring gear 109 is engaged, but the spline spur gear 106 is reversed by the spline piston 107 to turn the cubic. Engaging with the coupling 108, the spline spur gear 106 is in a disengaged state from the ring gear 109, so that the rotation connected to the small gear 114 as shown in FIG. 1A The tool 120 is not in a self-rotating operation for milling or boring.

On the other hand, the operation of the rotary tool 120, as shown in Figure 1b, when the hydraulic pressure is injected into the hydraulic inlet b 118 through a hydraulic controller (not shown) located outside the frame 10 It is as follows.

The hydraulic pressure flows into the hydraulic chamber a 123 by the inflow of the hydraulic pressure into the hydraulic inlet b 118 and the inflow hydraulic pressure causes the piston cubic coupling 110 to retreat to fix the bolt in the frame 10. Coupling 111 and the turning cubic coupling 108 are meshed to determine the position of the tool by hydraulic pressure to stop at the correct position and to machine the workpiece.

In order to transmit power to the rotary tool 120, the hydraulic pressure is injected into the hydraulic chamber a 123 through the hydraulic inlet b 118, and the hydraulic pressure is injected into the hydraulic chamber a 123 and at the same time, the piston cubic coupling 110 retreats. As the piston cubic coupling 110 is interlocked with the retraction, the hydraulic pressure flows into the hydraulic chamber d 126 and the spline piston 107 moves forward.

The spline piston 107 moves the spline spur gear 106 whose rear surface is fixed by the bearing 127, and the moved spline spur gear 106 is engaged with the ring gear 109.

In addition, the ring gear 109 is supported by a needle bearing 135 installed on the inner circumferential surface of the flange 133 fixed to the frame 10, thereby applying power to the small gear 114 supported by the bearing on the opposite side. Will be delivered.

Looking at the power transmission path in sequence, the rotational power of the drive motor 101 is transmitted to the first outer tooth spur gear 103, the first outer tooth spur gear 103 is a spur gear 105 in which the rotational power is engaged Deliver to

The spur gear 105 transmits rotational power to the spline spur gear 106 engaged with the spline, and the spline spur gear 106 sequentially transmits power to the ring gear 109 and the small gear 114. To allow machining of the workpiece with the rotary tool 120. On the other hand, the small gear 114 and the ring gear 109 are always engaged, and as shown in FIG. 1A, the disk 119 rotates. If the rotary tool 120 does not rotate itself (of course, if the disk 119 rotates, the rotary tool 120 does not rotate itself, but rotates like the disk 119), and FIG. As shown, the rotary tool 120 rotates itself and engages in all cases, such as when the disk 119 does not rotate. In other words, the spline spur gear 127 retracts to pivot. When engaged with the coupling 108, the bolt 50 The disk 119 is rotated (in this case, the small gear 114 is not rotated by being disengaged from the ring gear 109), the spline spur gear 127 is advanced to the ring gear 109 And the ring gear 109 rotates the small gear 109 to rotate the rotary tool 120 itself (in this case, the disengagement with the orbital pivotal coupling 108, the disk 119 does not rotate) The turret head and the rotary tool are selectively rotated while repeating the process.

The present invention can drive the automatic tool exchange and power transmission of the rotary tool selectively with a single drive motor, simplify the control by reducing the number of parts, simultaneous operation by one inflow and outflow of hydraulic pressure Reduce tool change time. In addition, it is possible to minimize the volume of the housing by reducing the number of parts installed in the housing, and there is an effect that can be used in the standard tool set of the turret lathe and turn mill vertical lathe tool bar.

Claims (5)

Turret head device for installing the drive motor 101 on the rear of the frame 10 and selectively driving the automatic tool change and the operation of the rotary tool 120 due to the indexing of the disk 119 by the power of the drive motor 101 To Receives rotational power from the drive motor 101 and is engaged with the first outer tooth spur gear 103 formed on the peripheral side of the motor shaft 102 and the peripheral side of the first outer tooth spur gear 103. A spur gear 105 having a spline portion formed therein, a cylinder portion 104 located at an outer circumference of the spur gear 105, The pivotal coupling 108 engaged with the splined gear 106 during the reverse operation by hydraulic pressure, and the splined gear 106 during the forward operation of the cylinder 104; A ring gear 109 engaged with and interlocked with A fixed cubic coupling 111 formed on an inner surface of the pivotal coupling coupling 108 and the ring gear 109 and integrally coupled to the frame 10 by a bolt 12, and the pivoting coupling coupling 108 A tooth is formed on the side opposite to the tooth of the fixed cubic coupling 111, and the piston cubic coupling 110 is coupled or spaced forward or backward by inflow and outflow of hydraulic pressure, The sequentially coupled piston cubic coupling 110 and the fixed cubic coupling 111 and the inner surface of the frame 10 and the disk 119 in front of the frame 10 to rotate the needle bearing 135 Supporting second shaft 112, Turret head device, characterized in that it is installed on the side of the housing 10 and comprises a small gear 114 for transmitting rotational power to the rotary tool 120 in conjunction with the ring gear (109). The method of claim 1, The cylinder portion 104, A spur gear 105 having a predetermined tooth on the rear side of the outer edge and forming a hollow portion 105a on the inner surface thereof, A spline spur gear 106 formed inside the spur gear 105 and constrained to a side to drive forward or backward; A piston coupled to the rear surface of the spline spur gear 106 and interlocked with the piston cubic coupling 110 at the same time by the inflow and outflow of hydraulic pressure, the piston forward or backward in the opposite direction to the piston cubic coupling 110 ( Turret head device characterized in that it further comprises. The method of claim 1, The cylinder part 104 further comprises forming a hydraulic chamber c (125) and a hydraulic chamber d (126), respectively, on the rear surface of the frame (10) for outflow and inflow of hydraulic pressure. The method of claim 1, The piston cubic coupling 110, When backing by hydraulic pressure, it engages with the fixed curb coupling 111 and the turning curb coupling 108 to prevent flow during the stop operation of the turret head, and simultaneously performs gear shifting operation of the spline spur gear 106. Turret head device further comprising the step of reducing the operating time. The method of claim 4, wherein Turret head device, characterized in that further comprising forming a hydraulic chamber a (123) and a hydraulic chamber b (124) which is a space for the outflow and inflow of the hydraulic pressure respectively on the front and rear of the piston cubic coupling (110).