JPS6114803A - Diameter control tool - Google Patents

Abstract

PURPOSE:To enable a tool to perform its machining in high accuracy and high efficiency, by clamping a slide by the wedge action while removing a gap from a sliding part of the slide and/or backlash from a driving system of the slide. CONSTITUTION:If a cam shaft 26 rotates in the direction of an arrow head (i), a shaft 18 moves in a direction (e) by the action of a spring 20 by separating the cam surface of a cam 27 from the shaft 18, and a slide 16 is clamped by the wedge action by adapting a tilt surface 18a to a tilt surface 16h. A shaft 19, to which the surface of a cam 28 is adapted by rotating the shaft 26 further in the direction (i), moves in a direction (h) removing backlash in a feed driving gear of the slide 16 through a rack 22 and a pinion 24, and the above described end is attained.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a diameter control tool that can adjust the machining diameter.

In recent years, complex production systems (F, M, S:
Flexible Manufacturing System
With the shift to STEM, the following two demands are becoming stronger.

(1) I want to reduce the number of tools. A large number of tools are required to carry out various types of machining, but there is a limit to the number of tools that can be stored in the automatic tool changer of machine tools such as masonning centers, which makes unmanned machining difficult. Too bad the range is limited. Therefore, we would like to reduce the number of tools by making it possible to process many different diameters with one tool.〇(2) By making it possible to automatically adjust the position of the cutting edge of the tool, it is possible to reduce the need for the operator to adjust the position of the cutting edge. I want to get rid of it and make it unmanned. For example, in polling machining, there are unavoidable problems such as differences from the preset position, tool wear, changes in the position of the cutting edge when replacing the indexable insert, and bending of the boring bar. Work is being carried out to determine the needle side. Automation of the measurement of the machined hole diameter has become possible with almost no problems due to the development of excellent touch sensors in recent years, but if the judgment result is not within the required dimensional tolerance, the position of the cutting edge must be adjusted accordingly. No. It is desirable to automate this blade edge position adjustment work. A diameter control tool as shown in FIG. 1 is known as a tool that meets these demands.

In FIG. 1, a diameter control tool 1 is configured such that its noyank portion 2 is rotated around a main shaft 3 of a machine tool so that it can be attached to the machine tool. Inside the holder body 4 of the diameter control tool 1, a screw shaft 5 is supported by a bearing (not shown) in a direction perpendicular to the rotation center axis of the holder body 4, and a gear 6 fixed to one end of the screw shaft 5 is supported. The screw shaft 5 is rotationally driven by driving the drive shaft 9 of the differential gear device 7, which is meshed with the gear 8 of the differential gear device rNL7 and is exposed outside the holder body 4 of the diameter control tool 1, using a known technique. It looks like this.

On the other hand, a slide 11 is slidably attached to a guide surface 10 provided in the front part of the holder body 4 in parallel with the screw shaft 5, and a female thread formed on the rear protrusion of the slide 1 is attached to the screw shaft 5. The slide 11 is screwed into the guide surface 10 by the rotation of the screw shaft 5, and the slide 11 is moved into the guide surface 10 as indicated by the arrow a or b.
The drive positioning is performed in the direction of . Furthermore, slide 1 has a tip 12 attached to its tip, and a digit bite holder 13 is fixed thereon.As arrow a and 7t of p1 slide 11 is driven and positioned in direction b, the tip of tip 12 also moves in the direction of arrow C or d. Drive positioning.

However, this conventional diameter-side tool 1 had the following two problems.

The first problem is that the support rigidity of the slide 11 is small.
This makes high-efficiency machining difficult. That is, slide 1
In order for 1 to be able to slide against the guide surface 10, a certain amount of clearance is required between the guide surface 10 and the cutting force that the tool holder 13 receives, and the tool holder 1
3. Slide 11 due to the centrifugal pressure received by slide 1
is displaced within the sliding gap between the guide surface 10 and becomes unstable. Furthermore, the pack rack between the screw shaft 5 and the female thread of the slide 11 also makes the stopping position of the slide 11 unstable. Since the slide 1lfi is supported through the so-called "backlash element", the support rigidity is small, and the
If high-efficiency machining with large displacements is performed, chatter vibration will occur.

The second problem is that the positioning accuracy of the slide 11 is poor, making it difficult to perform highly accurate and stable machining. As mentioned above, since the slide 11 is supported via the side element J, the cutting force and centrifugal force acting on the slide 11 vary depending on cutting conditions, degree of tool wear, and spindle speed. This is because the position of the slide 11 becomes unstable.

The present invention has been made in view of the above-mentioned problems with conventional diameter control tools. The purpose of the present invention is to provide a diameter control tool that has increased support rigidity and enables highly efficient and highly accurate machining.

To achieve this object, the diameter control tool according to the present invention has a structure in which a tool holder is fixed, and a slide is attached to the holder body so as to be slidable in a direction perpendicular to the rotation center axis of the holder, and the slide A diameter control tool comprising a feed drive device for driving and positioning the slide, the first and second shafts being slidably attached to the slide in a direction perpendicular to the direction of the moving force of the slide; ,
a first spring that biases the first shaft and presses and clamps the slide by the first shaft against its sliding guide surface; a first cam that is moved against a spring force to release the clamp on the slide; and a first cam that is removably engaged with the second shaft and that applies the moving force to the slide as the second shaft moves. a gear mechanism that applies a force in the direction;
a second spring that biases the second shaft to move the second shaft to disengage the gear mechanism and the second shaft; and a second spring that is driven in conjunction with the first cam. and after the first cam is separated from the first shaft and the slide is clamped, the second shaft is moved against the spring force of the second spring and the second shaft is moved through the gear mechanism. a second clamping the slide in the direction of its moving force;
It has six features: a cam;

An embodiment of the present invention will be described in detail below with reference to FIGS. 2 and 3. FIG. 2 is a longitudinal sectional view of a main part of a diameter control tool according to an embodiment of the present invention, and FIG. 3 is a sectional view taken along line AA in FIG.

In FIG. 2, a daughter shank portion (not shown) is provided at the base (lower part in the figure) of the holder body 14, and the shank portion is fitted onto the main shaft of the machine tool in the same manner as in the past, so that the holder body 14 can be attached to the machine tool. It is designed to be installed on. A guide surface is formed in the external portion of the holder body 14 along a direction perpendicular to its rotation center axis (perpendicular to the plane of the paper), and a slide 16 with a bite holder 15 fixed thereto can freely slide. Installed. In addition, the holder body 1
4, a screw shaft 17 is supported adjacent to the slide 16 and parallel to the amount of sliding force, and the rear protrusion 16 of the slide 16
An internal thread formed in a is threadedly engaged with the threaded shaft 17.

The screw shaft 17 is connected to a known feed drive device such as a differential gear device (not shown), so that when the screw shaft [7] rotates, the slide 16 is driven and positioned in a direction perpendicular to the plane of the paper. ing.

The holder main body 14 has a slide 16 sandwiched therebetween at symmetrical positions with respect to its rotation center axis, and has a first and a second 7 yen)18.
The first and second shafts 18, 19 are attached in the proximal direction (arrows e, g) by first and second springs 20, 21, respectively. is energized by 1st/Gift 18
A notch 18b having an inclined surface 18a is provided on the side facing the slide 16.
A sloped surface 16b having the same slope angle as the sloped surface 18a is formed on the side facing the shirt 18. When the first shaft e 8 moves in the direction of the arrow e by the spring force of the first spring 20, both the inclined surfaces 16b and i8a engage with each other, and the slide 16 moves into the holder main body 4 due to the force of the rotation. By moving the first shaft 18 in the force direction of the arrow f against the spring force of the first spring 20, both #
4. The engagement between the four slants 16b and 18a is released. Incidentally, the inclined surface 16 of the slide 6 bV3. , has a sufficient width along the direction of its movement force so as not to interfere with the first shaft ``8'' during a predetermined stroke movement of the slide 16; On the opposite side, when the slide 16 moves a predetermined stroke, a second
A notch 16C having a sufficient width is provided along the direction of the moving force so as not to interfere with the shaft 19 of the slide I6, and a notch 16C is provided on the rear surface of the slide I6 adjacent to the notch 16c along the direction of the moving force. The rack 22 is fixed. Further, two pinions 24 and 25 are fixed to the pinion shaft 23 supported by the holder body 14, and the second force pinion 24 is engaged with the rack 22 of the slide 16, and the second force pinion 25 is engaged with the rack 22 of the slide 16. It faces the shaft 19 of No. 2.

As shown in FIG. 3, the second shaft 19 has a chic 19a that engages with the pinion 25, and a notch 19 in front of the chic 19a.
When the pinion 25 is moved in the direction of the arrow g by the spring force of the second spring 21, the pinion 25 is disengaged from the rack 19a, By moving the second shaft 19 in the direction of the arrow against the spring force of the second spring 21, the rack 19a of the second shaft 19 and the pinion 25 engage, and the axis of the second shaft 19 is moved. Due to the force in the direction of force, the pinion shaft 23,
The slide 16 is urged along the direction of the moving force via the pinion 24 and the rack 22.

Further, a camshaft 26 is supported on the holder main body 14 on the proximal end side of the first and second shirts 18 and 19, and the first and second shafts is and i9 are respectively supported on the camshaft 26.
First and second cams 27, 28 are fixed, which abut against the proximal end surfaces of. The first and second cams 27.28 are in contact with the proximal surfaces of the first and second springs 18.19 with an angular spacing of about 180 degrees from each other, and the first and second cams 27.
18.19 against 0.21
The traps are designed to move in the force direction of arrows f and h, respectively. Note that when the second cam 28 pushes up the second shaft 19, the angle of the tangent to the second cam 28 at the contact point between the second cam 28 and the second shaft 19 is less than or equal to the friction angle. In this way, the second shaft 19 is pushed up by the wedge action, and the second cam 28 is prevented from being turned in the opposite direction by the reaction force of the second shaft 19 during rotation of the main shaft, thereby preventing the clamping force from loosening. .

In such a configuration, in the diameter control tool according to the present invention, when the first cam 27 is in contact with the first shaft 18 and the second cam 28 is separated from the second shaft 19, the feed drive device (not shown) is operated. Slide 1
6 and adjust the position of the cutting edge to a desired position.

Thereafter, when the cam shaft 26 is rotationally driven in the direction of arrow i from the outside of the holder main body 14 by a drive device (not shown) based on a known technique, the cam surface of the first cam 27 is moved away from the first shaft 18. Displace. As a result, the first jacket 18 is moved in the direction of arrow e by the action of the first spring 20, and the inclined surface 18a of the first shaft 18 is pressed against the inclined surface 16b of the slide 6, due to the wedge action. Slide 16 is clamped. Furthermore, when the camshaft 26 continues to be rotated in the direction of the arrow l, the second cam 28
The cam surface of the second cam 2 comes into contact with the second shaft 19, and the second cam 2
8, the second shaft 19 is moved in the direction of the arrow against the spring force of the second spring 21, and the rack 1
9a and the pinion 25 engage, the pinion 25 rotates, and the slide 6 receives a force in the direction of the moving force via the pinion shaft 23, pinion 24, and rack 22, and the slide 1
The balaclaran of the feed drive device No. 6 is removed.

- Release of the blade and clamp is performed in the completely reverse order to the above by rotating the camshaft 26 in the direction of the arrow j.

As described above in detail with reference to one embodiment, according to the present invention, it is possible to eliminate the gap in the sliding part of the slide and the para-fludge in the feed drive system of the slide, so that the support rigidity of the slide can be increased. , it is possible to perform high-precision machining with a stable cutting edge position even against fluctuations in centrifugal force and cutting force, and with improved support rigidity, it is possible to perform highly efficient machining with a large reduction in cutting depth. Become. -For force and slide clamps, first clamping is performed to eliminate the sliding gap on the guide surface, and then the balaclaran of the feed drive system is removed, and in addition, the direction of the clamp to eliminate the sliding gap is Since the direction is perpendicular to the direction of the moving force of the slide, the accuracy of stopping the cutting edge of the cutting tool holder is hardly impaired by the clamping operation.

In addition, regarding the rotation center axis of the first and second shafts, etc.,
By arranging them symmetrically, it is possible to reduce vibrations caused by unbalanced masses during high-speed rotation. Furthermore, the interlocking first and second cams sequentially remove the sliding gap of the p-slide and the paraclaran of the feed drive system, so the advantage is that the drive device can be simplified. There is.

[Brief explanation of drawings]

Fig. 1 is a cutaway front view of a conventional diameter control tool, Figs. 2 and 3 are an embodiment of the present invention, and Fig. 2 is a vertical sectional view of the main parts of the diameter control tool according to the present invention. , FIG. 3 is a sectional view taken along line AA in FIG. 2. In the drawings, 14 is the holder body, 15Vs is the bite holder, 16 is the slide, 17 is the screw shaft, 18 is the first shaft, 19 is the second shaft, 20 is the first spring, 21 is the second spring, 22 is a rack, 23 is a pinion shaft, 24.25 is a pinion, 26 is a cam shaft, 27 is a first cam, and 28 is a second cam - Patent applicant: Mitsubishi Heavy Industries, Ltd. Tawara, patent attorney, Ishi Ishi Shibu (song name) Figure 1 B Figure 2 A, J

Claims (1)

[Claims] In the diameter control tool, the tool holder is fixed, and the diameter control tool is equipped with a slide attached to the holder body so as to be slidable in a direction perpendicular to the rotation center axis of the tool holder, and a feed drive device for driving and positioning the slide. first and second shafts that are attached to sandwich the slide so as to be slidable in a direction perpendicular to the direction of movement of the slide; and biasing the first shaft to cause the slide to be moved by the first shaft. a first spring that presses against and clamps the slide guide surface; and a first spring that moves the first shaft against the spring force of the first spring to unclamp the slide.
a cam, a gear mechanism that removably engages with the second shaft and applies a force in the direction of movement to the slide as the second shaft moves; and a gear mechanism that biases the second shaft. a second spring that moves the second shaft to disengage the gear mechanism and the second shaft; and a second spring that is driven in conjunction with the first cam and that moves the first cam to After the slide is clamped away from the first shaft, the second shaft is moved against the spring force of the second spring to clamp the slide in its direction of movement via the gear mechanism. A diameter control tool comprising: a second cam.