JP2001062631A - Tapping machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To speed up a tapping machining and improve a tapping machining efficiency. SOLUTION: This tapping machine is provided with a rotation transmission mechanism 14 for transmitting the rotary power generated by the drive of a drive motor 31 to a main spindle 49, a speed change mechanism 16 for converting the rotary power of the drive motor 31 branchingly transmitted through the input shaft 82 operatively connected to the rotation transmission mechanism 14 to a prescribed rotary speed and for transmitting to the outside through an output shaft 85 and a feed mechanism 15 operatively connected to the output shaft 85 and for transmitting to the main spindle 49 after converting the rotary motion of the output shaft 85 to the reciprocating straight line motion along a tapping direction. Thereby, the speed up of the tapping machining is carried out while differing from the usual tap lead type tapping machine and the tapping machining efficiency can be improved.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a structure of a tapping machine for cutting a female screw by screwing a tap into a prepared hole formed in a workpiece.

[0002]

2. Description of the Related Art Many tapping processes using a conventional tapping machine employ a tap lead system. That is, when the tip of the tap is cut into the prepared hole formed in the workpiece, the tap advances while processing the thread by itself. When the tap is advanced to the predetermined tapping depth and the tap is rotated in the reverse direction, the tap retreats along the thread and the tapping process ends.

[0003]

However, in the tapping processing by the conventional tapping machine, when the rotation of the tap and the feed are not synchronized, a feed pitch error occurs and the female screw is enlarged. was there.
Also, many tapping devices such as tap chuck holders are configured for tap lead systems.

[0004] For this reason, the speeding up of tapping by a conventional tapping machine affects the thrust of the tap and the accuracy of the female screw is not stable, and the life of the tap is often significantly reduced. Therefore, it is difficult to increase the speed of the tapping process using the conventional tapping machine, and there is a problem that the tapping process efficiency is reduced.

The present invention has been made to solve the above problems, and an object of the present invention is to provide a tapping machine capable of increasing the speed of tapping processing and improving tapping processing efficiency. .

[0006]

According to a first aspect of the present invention, there is provided a rotation transmission mechanism for transmitting rotation power generated by driving a drive motor to a main shaft, and a branch transmission from the rotation transmission mechanism via an input shaft. A transmission mechanism that converts the rotational power of the drive motor into a predetermined rotational speed and transmits it to the outside via an output shaft, and converts the rotational motion of the output shaft into a reciprocating linear motion along the tapping direction and transmits it to the main shaft. The gist is that a feed mechanism is provided.

According to a second aspect of the present invention, in the first aspect of the present invention, the feed mechanism is provided with a biasing means for constantly biasing the main spindle in the anti-tapping direction during the tapping process. The gist of the invention is that when the feed power from the drive motor in the tapping direction is cut off, the urging means can move in the anti-tapping direction.

According to a third aspect of the present invention, in the second aspect of the present invention, the urging means is integrally movable with a cylinder provided in a main body case with respect to a main shaft and in a tapping direction in the cylinder. And a piston rod movably provided in the anti-tapping direction, wherein the piston rod is urged in the anti-tapping direction by receiving the pressure of the working fluid supplied from the outside into the cylinder. The gist of what has been done.

According to a fourth aspect of the present invention, in the invention according to any one of the first to third aspects, a speed ratio between an input shaft and an output shaft in the speed change mechanism is controlled by a main shaft. The gist is that the setting is made such that the feed of one tap pitch is performed for one rotation of the mounted tap.

According to a fifth aspect of the present invention, in the first aspect of the present invention, the input shaft and the output shaft of the speed change mechanism are connected to a rotation transmission mechanism and a feed mechanism. The gist is that they are configured to be detachable.

According to a sixth aspect of the present invention, in the first aspect of the invention, when an excessive torque is applied to the feed mechanism via an output shaft, The gist of the invention is to provide an overload limiting mechanism for interrupting transmission of feed power to the main shaft. (Operation) Therefore, in the first aspect of the present invention, the rotational power generated by driving the drive motor is transmitted to the main shaft via the rotation transmission mechanism. The rotational power of the drive motor is branched and transmitted to the speed change mechanism via an input shaft operatively connected to the rotation transmission mechanism, converted to a predetermined rotational speed, and transmitted to the outside via an output shaft. The rotational motion of the output shaft is converted into a reciprocating linear motion along the tapping direction by a feed mechanism operatively connected to the output shaft and transmitted to the main shaft. That is, the rotation of the main shaft and the feed are mechanically synchronized via the speed change mechanism.

According to the second aspect of the present invention, in addition to the operation of the first aspect, during the tapping process, the main shaft is constantly urged in the anti-tapping direction by the urging means. For this reason, even when a slight time difference occurs between the start of rotation of the main shaft and the start of feed when the main shaft is retracted, the main shaft is moved in the anti-tapping direction by the urging force of the urging means. That is, even if the feed power of the drive motor is not transmitted, the main shaft moves in the anti-tapping direction.

According to a third aspect of the present invention, in addition to the operation of the second aspect, during the tapping process, the piston rod receives a pressure of a working fluid supplied from the outside into the cylinder and receives the piston rod. It is urged in the tapping direction.
Therefore, when the main shaft is moved backward, the main shaft moves in the anti-tapping direction by the pressure of the working fluid until the feed power is transmitted from the drive motor to the main shaft. Therefore, despite the simple configuration, there is no small time difference between the time from the drive of the drive motor to the start of the rotation of the spindle and the time from the drive of the drive motor to the start of the feed operation of the spindle.

According to a fourth aspect of the present invention, in addition to the operation of the first aspect of the present invention, the number of taps per rotation of the tap mounted on the spindle is one.
The gear ratio of the speed change mechanism is set so that the feed for the pitch is performed. For this reason, a feed error is reduced, and expansion of the female screw is less likely to occur.

According to a fifth aspect of the present invention, in addition to the function of the first aspect, the input shaft and the output shaft of the speed change mechanism are connected to a rotation transmission mechanism. Operatively connected to the feed mechanism and the feed mechanism. Therefore, the transmission mechanism can be exchanged for one having a different speed ratio.

According to a sixth aspect of the invention, in addition to the function of the first aspect of the invention, an excessive torque is applied to the feed mechanism via an output shaft. Then, the transmission of the feed power to the main shaft is cut off by the overload limiting mechanism. For this reason, the tap mounted on the spindle is not excessively fed.

[0017]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment in which the present invention is embodied in a tapping machine will be described below with reference to FIGS.

As shown in FIG. 1, the tapping machine 11
Is provided with a main body case 12, and a drive mechanism 13, a rotation transmission mechanism 14, and a feed mechanism 15 are provided inside and outside the main body case 12.
And a speed change mechanism 16. (Main body case) An overhang portion 21 is formed on an upper portion of the main body case 12 so as to protrude to the side.
Inside 2, an upper partition 22 and a lower partition 23 are formed at predetermined intervals along the central axis O of the main body case 12, respectively. Upper end of upper partition 22 and body case 1
2 is separated from the inner top surface by a predetermined distance. The lower partition wall 23 is formed to extend upward from the bottom surface of the main body case 12. (Drive Mechanism) The drive mechanism 13 includes a drive motor 31. The drive motor 31 is fixed to the lower surface of the overhang 21 via a motor flange 32. The output shaft 33 of the drive motor 31 is connected to the motor flange 32 and the overhang portion 21.
And is connected to a motor pulley 34 arranged in the overhang portion 21. (Rotation transmission mechanism) The rotation transmission mechanism 14 is a main shaft pulley 4
The main shaft pulley 41 is disposed above the upper partition 22 in the main body case 12. The center axis of the main shaft pulley 41 is parallel to the center axis of the motor pulley 34. A V-belt 42 is mounted between the motor pulley 34 and the main shaft pulley 41. A pulley shaft 43 is connected to the main shaft pulley 41 so as to extend downward.

Bearings 44 and 45 are fixed between the upper and lower portions of the side surface of the upper partition 22 on the side of the projecting portion 21 and the inner surface of the main body case 12, respectively.
A pulley shaft 43 is rotatably inserted through 5. An upper spline hole 46 and a lower spline hole 47 are formed in the upper and lower portions of the pulley shaft 43, respectively.

One end of a spline shaft 48 is inserted into the lower spline hole 47 slidably up and down along the lower spline hole 47. The other end of the spline shaft 48 passes between the side surface of the projecting portion 21 of the lower partition wall 23 and the inner side surface of the main body case 12 and protrudes from the bottom surface of the main body case 12 to the outside. A main shaft 49 is provided at an outer end of the spline shaft 48, and a high-speed tap 50 is gripped and fixed to the main shaft 49 via a collet chuck 49a. The high-speed tap 50 is a metric right-hand thread tap. (Feeding Mechanism) The feeding mechanism 15 is provided with a hollow cylindrical quill 51 as a piston rod. The quill 51 is mounted on the spline shaft 48 so as to cover a portion of the spline shaft 48 protruding from the pulley shaft 43. The quill 51 includes a small-diameter portion 52 and a large-diameter portion 53. Bearings 54 and 55 are fixed to the innermost portion and the lower end opening inside the large diameter portion 53, and the spline shaft 48 is attached to both bearings 54 and 55.
Are rotatably inserted and supported.

A rear metal 56 and a front metal 57 are hermetically fixed between the upper and lower portions of the lower partition wall 23 on the side of the projecting portion 21 and the inner surface of the main body case 12, respectively. The small-diameter portion 52 and the large-diameter portion 53 of the quill 51 are vertically slidably inserted into the two metals 56 and 57, respectively. The lower portion of the large diameter portion 53 of the quill 51 projects outward from the lower surface of the front metal 57, and the main shaft 49 projects from the lower surface of the large diameter portion 53.

An annular flange 58 is formed on the outer periphery of the upper portion of the large diameter portion 53, and an O-ring 59 is mounted on the outer periphery of the flange 58. The collar 58 is made of metal 56, 5
Cylindrical pipe 60 as a cylinder disposed between
An O-ring 59 is formed so as to be able to slide up and down in a state in which the O-ring 59 is in tight contact with the inner peripheral surface of the O-ring.

Inner side surface of the main body case 12, lower partition 2
3, a space S1 is formed from the side surface of the projecting portion 21 side, the lower surface of the rear metal 56, the outer wall of the small diameter portion 52, the upper surface of the large diameter portion 53, the upper surface of the flange portion 58, and the inner peripheral surface of the pipe 60. Yes,
The internal pressure of the space S1 is always about atmospheric pressure.

The outer wall of the large diameter portion 53, the front metal 5
7, a space S2 is formed from the lower surface of the flange portion 58 and the inner peripheral surface of the pipe 60. The space S2 is connected to a compressor (not shown) outside the tapping machine 11, and compressed air as a working fluid generated by the compressor can be supplied into the space S2.

The inner wall of the main body case 12 and the lower partition 2
3, side surface of the projecting portion 21, quill 51, rear metal 5
6. A cylinder mechanism M as an urging means is constituted by the front side metal 57, the flange 58, the O-ring 59, the pipe 60, the compressor (not shown), and the like.

On the other hand, a rotation transmitting shaft 71 is disposed between the motor pulley 34 and the main shaft pulley 41 so as to extend along the center axis O of the main body case 12. Are formed. The rotation transmission shaft 71 is a bearing 7 fixed between the upper portion of the side surface of the upper partition 22 on the side of the overhang portion 21 and the inner surface of the main body case 12.
3 rotatably supported. The lower end of the rotation transmission shaft 71 protrudes from the lower surface of the bearing 73.

A ball screw 74 is provided below the rotation transmission shaft 71 so as to be along the center axis O of the main body case 12. The ball screw 74 includes a bearing 75 fixed between a lower portion of the side surface of the overhang 21 on the upper partition 22 and an inner surface of the main body case 12, and a protrusion 2 on the lower partition 23.
It is rotatably supported by bearings 76 fixed between the upper part of one side surface and the inner surface of the main body case 12.
The upper end of the ball screw 74 protrudes from the upper surface of the bearing 75.

The lower end of the rotation transmission shaft 71 and the ball screw 7
The upper end of 4 is a torque clutch 7 as an overload limiting mechanism.
7 are connected. A ball screw nut 78 is screwed between the bearings 75 and 76 of the ball screw 74 so as to be able to advance and retreat relative to the ball screw 74.

A connection bracket 79 is provided on the ball screw nut 78 so as to protrude toward the spline shaft 48, and the tip of the connection bracket 79 is connected to the upper end of the small diameter portion 52. For this reason, the ball screw nut 78 and the quill 51 can be integrally moved.

The ball screw nut 78 is moved between the maximum retracted position A shown by a solid line in FIG.
Is movable between a maximum forward position B indicated by a two-dot chain line. When the ball screw nut 78 is at the maximum retracted position A, the spindle 49 is at the machining start position C shown by a solid line in FIG. When the ball screw nut 78 is at the maximum advance position B, the spindle 49 is at the deepest machining position D shown by a two-dot chain line in FIG.

At the time of tapping, the amount of movement of the ball screw nut 78 from the maximum retreat position A to the maximum advance position B, that is, the amount of movement of the spindle 49 from the processing start position C to the deepest processing position D is determined by the desired tapping. It is set appropriately according to the depth. Accordingly, the machining end position (not shown) of the spindle 49 at which the tapping to the desired tapping depth is completed.
Changes between the processing start position C and the deepest processing position D.

The maximum retreat position A and the maximum forward position B of the ball screw nut 78 are detected by a retreat end and forward end limit switch (not shown) comprising a proximity sensor or the like, respectively, and the maximum retreat position A and the maximum forward position of the ball screw nut 78 are detected. Movement beyond position B is prevented.

In this embodiment, downward movement of each member in FIG. 1 is referred to as forward movement, and upward movement is referred to as backward movement. 1 is referred to as a tapping direction, and the upper side in FIG. 1 is referred to as an anti-tapping direction. The tapping direction refers to a direction in which a female screw is cut into a prepared hole (not shown) formed in a workpiece (not shown). (Transmission mechanism) As shown in FIGS.
Is arranged on the upper part of the main body case 12. Transmission mechanism 1
6 includes a gear case 81 in which a driving gear 83 mounted on an input shaft 82, a plurality of intermediate gears 84, and a driven gear 86 mounted on an output shaft 85 are accommodated. Each of the gears 83, 84, 86 is provided with a drive gear 8
The gears are appropriately meshed so that the rotational force of No. 3 is transmitted to the driven gear 86 via each intermediate gear 84. The input shaft 82 and the output shaft 85 penetrate the lower surface of the gear case 81 and the upper surface of the main body case 12 and protrude to the outside.

The input shaft 82 and the output shaft 85 are connected to the upper spline hole 46 of the pulley shaft 43 and the rotation transmitting shaft 7 respectively.
One spline hole 72 is detachably spline-coupled. When the high-speed tap 50 makes one rotation,
The input shaft 82 and the output shaft 85 so that the ball screw nut 78 and the main shaft 49 can be accurately fed by one pitch of the high-speed tap 50 in the tapping direction or the anti-tapping direction without error.
, That is, the number of teeth and the pitch circle diameter of each of the gears 83, 84, 86 are set.

Next, the operation of the tapping machine 11 configured as described above will be described. Workpiece (not shown)
When tapping is performed on a prepared hole (not shown) formed in advance, compressed air generated by a compressor (not shown) outside the tapping machine 11 is continuously supplied to the space S2. For this reason, the internal pressure of the space S2 increases, and a force in the anti-tapping direction by the compressed air acts on the quill 51 and the main shaft 49 via the lower surface of the flange 58.

In this state, the tip of the high-speed tap 50 is cut into the prepared hole, and the drive motor 31 is driven. Then
The output shaft 33 of the drive motor 31 rotates forward, and this rotational force is directly transmitted to the high-speed tap 50 via the motor pulley 34, the V-belt 42, the main shaft pulley 41, the pulley shaft 43, the spline shaft 48, the main shaft 49, and the collet chuck 49a. Is transmitted to As a result, the high-speed tap 50 rotates forward.

On the other hand, the rotational force of the pulley shaft 43 is controlled by the input shaft 82, the driving gear 83, each intermediate gear 84, the driven gear 86,
The power is transmitted to the ball screw 74 via an output shaft 85 and a torque clutch 77. With the forward rotation of the ball screw 74, the ball screw nut 78 advances relatively to the ball screw 74. The movement of the ball screw nut 78 is transmitted to the quill 51 via the connection bracket 79.

The quill 51 moves forward against the pressure in the anti-tapping direction by the compressed air. As the quill 51 advances, the spline shaft 48, the main shaft 49, and the high-speed tap 50 also advance integrally. Therefore, high-speed tap 5
0 is fed in the tapping direction while rotating, and the high-speed tap 50 advances while cutting a female screw to the prepared hole of the workpiece.

In the present embodiment, the ball screw nut 78 moves forward accurately by one pitch of the high-speed tap 50 every time the high-speed tap 50 makes one rotation. That is,
In the tapping processing by the tapping machine 11, the rotation and the feed of the high-speed tap 50 are performed almost completely in synchronization.
For this reason, the feed error of the high-speed tap 50 is reduced, and expansion of the female screw is less likely to occur.

When the spindle 49 is rotated, the machining start position C
, A predetermined tapping depth is formed by the high-speed tap 50 in the prepared hole of the workpiece. Thereafter, when the drive motor 31 is driven to rotate in the reverse direction, the high-speed tap 50 retreats along the thread formed by itself.

In this embodiment, each time the high-speed tap 50 makes one rotation, the ball screw nut 78 is accurately retracted by one pitch of the high-speed tap 50 without error. Then, when the spindle 49 is retracted and returned from the machining end position to the machining start position C, the tapping of one prepared hole is completed.

Although the rotation of the main shaft 49 is performed by directly transmitting the power of the drive motor 31 as described above, the feed of the main shaft 49 is performed via the speed change mechanism 16. Between the driving gear 83 and each intermediate gear 84, between each intermediate gear 84, and between each intermediate gear 84 and the driven gear 86, an appropriate backlash is provided to smoothly rotate each gear 83, 84, 86. Is provided. For this reason, the time from the start of driving of the drive motor 31 to the start of rotation of the spindle 49, and the time from the start of drive of the drive motor 31 to the start of spindle 49
There is a slight time difference from the time until the start of feeding of the sheet.

The slight time difference between the start of rotation of the spindle 49 and the start of feed does not cause much problem at the start of tapping, but the tapping is completed and the spindle 49 is retracted from the processing end position to the processing start position C. In such a case, a problem such as expansion of the internal thread may occur. That is, when the tapping process is completed, the main shaft 49 rotates before the main shaft 49 is fed in the anti-tapping direction, and the high-speed tap 50 reversely rotates at the same position where the thread cutting is completed, so that the thread is shifted.

In this embodiment, a force in the anti-tapping direction due to the compressed air always acts on the main shaft 49 via the flange portion 58. Further, the frictional resistance between the ball screw 74 and the ball screw nut 78 is much smaller than a general sliding contact screw such as a triangular screw. Therefore, when a predetermined force acts on the ball screw nut 78, the ball screw nut 78 moves in the tapping direction or the anti-tapping direction. Then, the ball screw 74 rotates with the movement of the ball screw nut 78.

Therefore, even when a slight time difference occurs between the rotation start and the feed start of the main shaft 49 when the main shaft 49 is retracted, the main shaft 49 is moved in the anti-tapping direction by the pressure of the compressed air in the space S2. You. That is, even if the feed power of the drive motor 31 is not transmitted, the main shaft 49 moves in the anti-tapping direction. For this reason, the high-speed tap 50 does not reversely rotate at the same location where the thread cutting is completed.

When the feed power from the drive motor 31 is transmitted to the main shaft 49 with a slight delay from the start of the reverse rotation of the main shaft 49, the main shaft 49 moves backward with the movement of the ball screw nut 78. That is, the ball screw nut 78 is
Each time the high-speed tap 50 makes one rotation, the main shaft 49 retreats by one pitch of the high-speed tap 50 while suppressing the movement of the main shaft 49 in the anti-tapping direction due to the pressure of the compressed air.

In this way, almost complete synchronization between the rotation and the feed of the high-speed tap 50 is achieved. In addition, when an excessive torque is applied to the rotation transmission shaft 71 via the output shaft 85 for some reason during the tapping process, transmission of the feed power from the drive motor 31 to the main shaft 49 is interrupted by the torque clutch 77. Therefore, the tap 50 mounted on the main shaft 49 is not excessively fed.

Therefore, according to the present embodiment, the following effects can be obtained. (1) The rotational power generated by driving the drive motor 31 is transmitted to the main shaft 49 and transmitted to the feed mechanism 15 via the speed change mechanism 16. That is, the rotation and the feed of the main shaft 49 are mechanically synchronized by the transmission mechanism 16. Therefore, unlike a conventional tapping-type tapping machine, tapping can be speeded up and tapping efficiency can be improved. Further, there is no need to provide a plurality of drive motors 31 for rotation and feed, and a control device for synchronizing the plurality of drive motors 31 is not required. Therefore, the cost of the tapping machine 11 is lower than when a plurality of drive motors 31 are provided. Further, the configuration of the tapping machine 11 can be simplified.

(2) The feed mechanism 15 is provided with a cylinder mechanism M that constantly biases the spindle 49 in the tapping direction during tapping. Therefore, at the same point of the high-speed tap 50 due to a small time difference generated between the time from the driving of the drive motor 31 to the start of the rotation operation of the spindle 49 and the time from the drive of the drive motor 31 to the start of the feed operation of the spindle 49. Of the female screw is prevented, and a decrease in the accuracy of the female screw is alleviated. Therefore, despite the simple configuration, the rotation and the feed of the main shaft 49 can be almost completely synchronized.

(3) The speed ratio of the speed change mechanism 16 is set such that the feed for one pitch of the tap per rotation of the tap mounted on the main shaft 49 is accurately performed without error. For this reason, a feed error is reduced, and expansion of the female screw is less likely to occur. Therefore, it is possible to obtain an accurate female screw thread shape approximate to the high-speed tap angle shape. As a result, tapping can be performed at a higher speed and with higher precision than in the past. Incidentally, in the conventional tapping machine (not shown), the rotation speed of the spindle (tap) 49 is limited to about 1600 rpm, but according to the tapping machine 11 according to the present invention, the rotation speed of the spindle 49 is improved to about 4000 rpm. Can be done.

(4) The input shaft 82 and the output shaft 85 of the transmission mechanism 16 are configured to be detachable from the rotation transmission mechanism 14 and the feed mechanism 15, respectively. For this reason, the transmission mechanism 16 can be replaced with one having a different speed ratio. Therefore, it is possible to perform synchronous feed corresponding to each of a plurality of types of high-speed taps 50 having different pitches.

(5) The feed mechanism 15 has an output shaft 8
A torque clutch 77 is provided to cut off transmission of feed power to the main shaft 49 when excessive torque is applied via the clutch 5. For this reason, the tap 50 attached to the main shaft 49 is not sent excessively, and damage to the tap 50 and each part of the tapping machine 11 can be prevented.

The above embodiment may be modified as follows. In the present embodiment, the main body case 12 and the pipe 6
Although 0 is configured as a separate member, both 12 and 60 may be formed integrally. By doing so, the number of parts can be reduced.

In the present embodiment, the space S2
The main shaft 49 is configured to be biased in the anti-tapping direction by supplying compressed air from the compressor to the inside. However, as shown in FIG.
An elastic member such as 1 may be interposed, and the main shaft 49 may be urged in the anti-tapping direction by the elastic force of the spring 91. Even in this case, the time difference between the start of rotation of the main shaft 49 and the start of feed when the main shaft 49 retreats can be eliminated. Accordingly, rotation of the high-speed tap 50 at the same position is prevented, and a decrease in the accuracy of the female screw can be mitigated.

The high speed tap 50 may be replaced with a metric left screw tap. In this case, the transmission mechanism 1
6 and another speed change mechanism (not shown) configured to rotate the ball screw 74 in the opposite direction to the present embodiment. The speed change ratio of this other speed change mechanism is set such that feed of one tap is performed per one rotation of the tap. In this way, a high-precision left female screw can be formed. Further, the high-speed tap 50 may be replaced with an inch right screw or an inch left screw tap such as a unified screw tap, a wit screw tap, and a pipe screw tap. At this time, the speed change mechanism 16 is replaced with another speed change mechanism (not shown) provided with a gear having a tooth number that is a multiple of 25.4, which is a value obtained by converting one inch into millimeters. In the case of an inch left screw tap, the other transmission mechanism is configured to further rotate the ball screw 74 in the opposite direction to the present embodiment. With this configuration, the feed of the pitch of the inch tap is accurately performed per rotation of the inch tap, and a high-precision inch right female screw or inch left female screw can be formed with the ball screw 74 for the metric screw. Therefore, only by replacing the transmission mechanism 16, one tapping machine 1
Various kinds of female screws can be formed by the method 1.

Next, technical ideas other than the claimed invention which can be grasped from the embodiment will be described below together with their effects. A rotation transmission mechanism (14) for transmitting the input transmitted rotational power to the main shaft (49), and a feed mechanism (15) for converting the input transmitted rotational power to reciprocal linear motion and transmitting the same to the main shaft (49). In the tapping machine (11) provided with the above, the input side of the rotation transmission mechanism (14) and the input side of the feed mechanism (15) are operatively connected via a speed change mechanism (16), so that the rotation of the main shaft (49) and the feed are performed Tapping machine configured to synchronize. Even in this case, the rotation of the main shaft and the feed are mechanically synchronized via the speed change mechanism, so that the speed of the tapping process can be increased and the tapping process efficiency can be improved.

[0057]

Therefore, according to the first aspect of the present invention, the rotation of the main shaft and the feed are mechanically synchronized via the speed change mechanism, thereby speeding up the tapping process.
Tapping efficiency can be improved.

According to the invention described in claim 2, according to claim 1
In addition to the effects of the invention described in (1), a minute time difference generated between the time from the driving of the drive motor to the start of the rotation operation of the spindle and the time from the drive of the drive motor to the start of the feed operation of the spindle is reduced. Accordingly, it is possible to prevent a decrease in the precision of the female screw due to a delay in feed of the spindle.

According to the invention described in claim 3, according to claim 2
In addition to the effects of the invention described in (1), despite the simple configuration, it occurs between the time from the drive of the drive motor to the start of the rotation operation of the spindle and the time from the drive of the drive motor to the start of the feed operation of the spindle. A minute time difference can be reduced.

According to the fourth aspect of the present invention, the first aspect is provided.
In addition to the effects of the invention described in the third aspect, the feeding error is reduced and the expansion of the female screw is less likely to occur, so that an accurate female screw peak approximate to the tap mountain can be obtained.

According to the invention of claim 5, according to claim 1,
In addition to the effects of the inventions set forth in the fourth to fourth aspects, since the transmission mechanism can be exchanged for one having a different transmission ratio, synchronous feed corresponding to a plurality of types of taps having different pitches can be performed.

According to the invention of claim 6, according to claim 1,
In addition to the effects of the inventions described in the fifth to fifth aspects, the tap mounted on the main shaft is prevented from being sent excessively, so that breakage of the tap can be prevented.

[Brief description of the drawings]

FIG. 1 is a front sectional view of a tapping machine according to an embodiment.

FIG. 2 is a sectional view taken along line 1-1 in FIG. 1;

FIG. 3 is a plan view of the tapping machine according to the embodiment.

FIG. 4 is a front sectional view of a main part of a tapping machine according to another embodiment.

[Explanation of symbols]

12: body case, 14: rotation transmission mechanism, 15: feed mechanism, 16: speed change mechanism, 31: drive motor, 49: spindle,
51: quill (piston rod), 59: pipe (cylinder), 77: torque clutch (overload limiting mechanism), 8
2 ... input shaft, 85 ... output shaft, C ... processing start position, D ... processing end position, M ... cylinder mechanism (biasing means).

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Jiro Miyagawa 1-1-1, Miyakawacho, Seki-shi, Gifu Miyagawa Industry Co., Ltd. (72) Inventor Tadashi Mori 1-1-1, Miyakawacho, Seki-shi, Gifu No.Miyagawa Industry Co., Ltd.

Claims (6)

[Claims] A rotation transmission mechanism (1) for transmitting rotation power generated by driving a drive motor (31) to a main shaft (49).
4) and an input shaft (8) operatively connected to the rotation transmission mechanism (14).
A transmission mechanism (16) for converting the rotational power of the drive motor (31) branched and transmitted via the second shaft (2) to a predetermined rotational speed and transmitting the rotation power to the outside via an output shaft (85); ), And a feed mechanism (15) for converting the rotational motion of the output shaft (85) into a reciprocating linear motion along the tapping direction and transmitting the reciprocating linear motion to the main shaft (49).
Tapping machine with 2. The feeding mechanism (15) is provided with an urging means (M) for constantly urging the main shaft (49) in the anti-tapping direction during the tapping process, and the main shaft (49) is provided with a drive motor. The tapping machine according to claim 1, wherein when the feed power from (31) in the tapping direction is shut off, the tapping machine is configured to be movable in the anti-tapping direction by the biasing means (M). 3. A cylinder (59) provided in a main body case (12).
And a piston rod (51) provided integrally movable with respect to the main shaft (49) and movable in the tapping direction and the anti-tapping direction within the cylinder (59), wherein the piston rod (51) is a cylinder. 3. The tapping machine according to claim 2, wherein the tapping machine is configured to be urged in the anti-tapping direction by receiving the pressure of the working fluid supplied from the outside into the inside. 4. A speed change ratio between an input shaft (82) and an output shaft (85) in the speed change mechanism (16) is determined by a main shaft (4).
The tapping machine according to any one of claims 1 to 3, wherein the tap (50) is set such that feed of one pitch of the tap (50) is performed per rotation of the tap (50) mounted on the (9). 5. An input shaft (82) of the speed change mechanism (16).
The tapping machine according to any one of claims 1 to 4, wherein the output shaft (85) is detachably attached to the rotation transmission mechanism (14) and the feed mechanism (15). 6. An output shaft (8) is provided on the feed mechanism (15).
An overload limiting mechanism (77) for interrupting transmission of feed power from the drive motor (31) to the main shaft (49) when excessive torque is applied via (5). The tapping machine according to any one of the above.