JPS58202769A - Fine feed mechanism for precision apparatus - Google Patents

Abstract

PURPOSE:To provide very fine feed of a precision apparatus without errors and enable it to endure sufficient feed load by fine feeding it with a movable head being interlocked with a rotating cam. CONSTITUTION:A head 2 urged to a base bed 1 in one direction is provided in the center with a rectangular hole 2A through which a cam shaft 3 extends. An approximately round cam 4 is eccentrically mounted on the cam shaft 3 so that its cam facet bears against a stopper fitting 5 fixed to a portion of the inner edge of the hole 2A. The rotation of the cam 4 pushes out the stopper fitting 5 according to its eccentricity to fine feed the head 2. This feed is applied to an end face grinder of optical fibers for example so that a grinding wheel is mounted on the head 2 and fine fed.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a fine movement feeder, and more particularly to a fine movement feeder that can be applied to precision processing equipment such as end face polishing of optical fibers, precision measurement equipment, and the like.

Conventionally, this type of precision processing equipment, precision machines (fine movement single tables such as scalers, and lIk movement feeders for movable heads)
Gradual feed was performed using precision small pitch screws. However, when feeding with such a small pitch screw with a close shaft, the thread pitch of the precision small screw is at most 1/2 inch even if it is machined to the minimum, and it is difficult to machine a thread pitch smaller than this.

In addition, since such small screw threads are inevitably small, the permissible load for fine-adjustment feeding is small, so the precision machined and precisely measured objects to which it can be applied are limited to lightweight and small objects. .

Furthermore, the fine movement feeder W (7) minimum feed (D, town, 5'
The ichromator scale is at most 0003~0.0/
mya (!; 0 to IO μm), and fine movement of less than that was impossible. Further, fine movement feed using a screw inevitably requires some play (gap) between the screws, and wear due to rotation of the screw is likely to occur, so that minute errors inevitably occur. Furthermore, it is very difficult to process small precision screws with high precision, and the cost is correspondingly high.

The purpose of the present invention is to solve the problems of the conventional fine movement feeding device as described above, and to be able to perform very fine gradual movement without causing errors, and to be able to withstand a sufficient amount of feeding carts.It is simple and inexpensive. An object of the present invention is to provide a fine movement feeding device.

According to the invention, such objects include: a movable head offset in one direction on a base; a fine adjustment camshaft rotatably provided on the base; and a fine adjustment camshaft rotatable together with the fine adjustment camshaft. is equipped with a circular fine adjustment cam,
The center of the fine adjustment cam is eccentric from the rotation center of the fine adjustment cam shaft, and the curved surface of the fine adjustment cam is in contact with the movable head in a state opposite to the shifting force,
This is achieved by a gradual movement feeder flK for a precision instrument, characterized in that as the fine adjustment cam shaft rotates, the movable head moves slightly against the shifting force by the action of the fine adjustment cam.

Next, the present invention will be described in more detail with reference to embodiments of the present invention based on the accompanying drawings.

*/The figure shows the principle of a fine movement feeder as an embodiment of the present invention. ! ! / [As shown in H, in the fine movement feeder of this embodiment, on the base 1,
A movable head 2 is installed in which a rectangular hole 2^ is provided in the center and springs 6 are provided in two spring receivers 2C on the lower surface 2B.

A fine adjustment cam shaft 3 with a small diameter (φB) and a fine adjustment cam 4 with a large diameter (φ^) are provided in the rectangular hole 2A, and the center point β of the fine adjustment cam shaft 3 and the center of the fine adjustment cam 4 are provided. Point 6 is X
Only the dimensions are eccentric.

Since the lower part of the fine adjustment cam 4 is constantly pressed upwardly by the spring 6, the movable head 2 is constantly in contact with the abutment fitting 5, which is a tooth fixed to the movable head 2.

In the fine-adjustment feeder configured as described above, first, the difference between the center points α of the front fine-adjustment cam 4 and the center point β of the fine-adjustment camshaft 3, that is, the X dimension, is temporarily set to O0θ! rm (! O
11m) (actually, it is possible to make the X dimension smaller), first attach the center point α to the highest point and rotate the fine adjustment cam shaft 3 and the fine adjustment cam 4, then the center point α moves around the center point β, and when the center point α reaches the lowest position, that is, when the center α moves from the highest position to the lowest position I:8 (half a rotation), the movable head 2 The moving distance is X dimension large - times 0.0!
;w.

C! ;Opm)X2=0. /lxc This means that it has moved 10100tt.

In this way, one fine adjustment force is 0.7wc1 with 40 and a half rotations.
Since it is possible to move the movable head 2 smoothly within a range of 00 μm (actually, small movements are also possible), a micrometer scale or a dial gauge is provided at the tip of the fine adjustment camshaft 3. By installing it, fine movement feed of about 0.00 mm/mm (7 μm) is easily possible.

FIG. 1 is a 1-meter view of a percussion feeding device as another embodiment of the present invention. That is, a pace table IK recess 1'A is provided, and the movable head 2 is installed in the recess IIA.

Since the movable head 2 has substantially the same configuration as that in FIG. 1, the description of the same configuration will be omitted. However, a steel ball 7 (or roll) is provided at the bottom of the fine adjustment cam 4 instead of the first V stopper 5, and the #goal 7 is fixed with a fixture 8 so as to be freely rotatable.

The fine movement feeder having such a configuration is as described above. - The sliding contact between the Luer and the fine adjustment cam 4 is due to the fact that both rotate and is a point contact, so the rotation is very smooth and the movement of the movable head 2 is also smoother. In addition, base stand II
Since the movable pace 2 fits snugly into the recess 1'^, the fine movement feeder can feed not only vertically up and down, but also horizontally from side to side or front to back.)1. ,
It is what it is.

FIG. 3 shows a fine movement feeder as another embodiment of the present invention. The fine-movement feed device of this embodiment incorporates a speed reducer using gears to enable even finer VCe feed. In this embodiment, the base 10 is provided with a movable head '#lO^ on the left side and a gear chamber 10B on the right side. Since it is the same as the movable head 2 shown in FIG. 1, detailed explanation will be omitted. In one gear chamber 10B, a worm gear 11 is provided approximately at the center of a fine adjustment cam shaft 3' extending from the fine adjustment cam 4 of the movable head 'll0A. The worm gear x[ciW
Worm gears 12 corresponding to each other at right angles are provided, and the rotational force is transmitted by the gears. A worm gear shaft 13 is connected to the wrinkled worm gear 12,
A micrometer (not shown) is attached to one tip side. and the worm gear 11
The gear ratio between the worm gear 11 and the worm gear 12 is such that the number of gears in the worm gear 11 is increased and the number of gears in the worm gear 12 is decreased.

For example, if the ratio is 70:/, when the worm gear 12 rotates S, the worm gear 11 rotates half a rotation K.

In such a fine movement feeder, as mentioned above,
The difference between the center point α of the fine adjustment cam 4 and the center point β of the fine adjustment cam shaft 3', that is, the x dimension, is 0.0! rxmc! ;0μm), the maximum movement amount of the movable head 2 is 0. /Sekho (100μm
), and if the worm gear does not rotate by S, it will be 0.7w (10
0 μm) will not move. In other words, the movable head 2 moves by 0.02 μm (20 μm) with the /l+o1 rotation of the worm gear 12, and the worm gear h
It is clear that the micro-movement feed device NY is capable of accurately feeding micro-movements of 0.00/m (7 μm) or less based on the scale of the micrometer attached to one end of the micrometer.

FIG. 9 shows still another embodiment of the present invention.
The worm gears 11 and 12 shown in the figure are replaced by flat gears. In other words, in the gear chamber 10B of the pace 10, a parallel gear 11A is provided on the fine adjustment camshaft 3', and a flat ear 12A is provided in parallel with the parallel gear 11A. It is connected to the parallel gear shaft 13^. A myrometer 15 provided outside the pace 10 is provided at one end of the parallel gear shaft 13A. In the gear wave speed mechanism configured in this way, the movable head 2, the fine adjustment cam 4, the fine adjustment cam shaft 3', the flat gears 11A, 12^, and the micrometer 15 are all arranged in parallel. Since there are many processing machines and measuring machines, such a horizontal fine movement feeder has a wide range of applications.

FIG. S is a partially cutaway schematic front view showing end face polishing and mounting of an optical fiber using the fine movement feeder of the present invention as described above, and FIG. 6 is a partially cutaway schematic diagram of the device shown in FIG. FIG. This end face polishing device mainly uses a base plate 3.
0, a rotary table 40, a laboratory placenta 50, a movable head 60, a fixed head 70, a motor 80, and a fine movement feeding device 90 according to the present invention.

A rotary table 40 and a fixed head 70 are identified on the base plate 30, and the rotary table 40 has an optical connector ferrule 20 connected to an optical fiber cable 25, which is a workpiece.
is attached by an end face fixing base 42. This ferrule 20 can be attached to and removed from the rotary table 40 as needed.

A rotary spindle 65 is mounted on the left side of the front fixed head 70.
A movable head 60 provided with a polishing disk 50 is provided so as to be inserted into and interposed with a female-shaped square guide 66 and a female-shaped V-shaped guide 71. Further, a motor 80 is fixed to the right side surface of the fixed head 70 with an identification bolt 82. Further, in the central portion 75 of the fixed head 70, a gear portion 91 of the fine movement feeder ft90 is provided.

A ring-shaped resinoid diamond grindstone 51 is provided at the bottom of the polishing disc 50, and the polishing disc 50 is connected to the spindle 6.
5 and ① pulley 67.

A spring water receiver 6 is provided on the lower surface 61 of the movable head 60.
2, a spring 63 is inserted into the spring water receiver 62, and the spring 63 is received by a swinging receiver 64.

The fixed head 70 has a front recess 7 on its outer front side.
2, on the rear surface thereof, a firefly recess 72' has a mounting portion 81 of a motor 80 fixed thereto by a gel 82.

The motor 80 is provided with a pulley 83 and a belt 84.
and (1) are connected at a pulley 67 so that rotational force is transmitted.

A fine adjustment handle 9 is provided in the front recess 72 of the fixed head 70.
A fine adjustment scale 93 and a handle shaft 94 are provided in front of the tTh handle 92, and a worm gear 95 is attached to the approximate center of the handle shaft 94 and can be rotated by a plurality of bearings 96. Fixed head 7
Fixed to 0. Corresponding to the worm gear 95,
A worm gear 97 having a rotating shaft substantially perpendicular to the worm gear 95 is provided. The worm gear 97 is
Fine adjustment cam shaft 100 of aX cam 99 by knock pin 98
Fixed. The fine adjustment camshaft 100 is rotatably fixed to the fixed head 70 by a plurality of bearings 101.

A fine adjustment fitting 102 fixed to the movable head 60 is provided at the lower part of the front F fine adjustment cam 99, and moves slightly up and down together with the movable head 60 as the fine adjustment cam 99 rotates.

The operation of polishing the ferrule 20 of the optical connector and the end face of the optical fiber inserted therein in the end face polishing apparatus having such a configuration will be described below. First, as clearly shown in FIG. 5, an optical connector ferrule 20 having optical fibers 25 connected thereto is attached to the side of the rotary table 40 using an end face fixing table 42.

Next, the motor 80 is rotated and the rotation is transmitted by the mill 84 to the polishing disk 50 to which the grinder 65 and the resinoid diamond grindstone 51 are attached.

The ferrule 20 mounted on the rotating table 40 and the end face 20/ of the optical fiber are brought into contact with the resinoid diamond grindstone 51 rotated by the front P motor 80 to polish the end face. In this case, the grinding cost of the end face is 0-00
It has dimensions on the order of 1 m, that is, minute dimensions on the order of /μm,
The vertical movement of the movable head must be able to read fine movement scales on the order of 700 minutes/μm. For this purpose, the fine movement feeding device 90 according to the present invention includes a worm gear 9.
The gear ratio between the worm gear 97 and the worm gear 97 is /:O. Furthermore, the difference between the center points α and β of the fine adjustment cam 100 and the fine adjustment cam shaft 99, that is, the X dimension is 0.3 mm and 300 μm)
It is said that The center point β of the fine adjustment cam shaft 99 is fixed, and as it rotates, the center point α of the fine adjustment cam 100 rotates around the center point β. Therefore, when the center point α of the fine adjustment cam 100 moves from the highest point to the lowest point, it moves by 0.4 wC600 μm). At this time, the fine adjustment handle 92 is adjusted as described above. :60, so if it rotates 30 times, the fine adjustment cam will turn half a turn, and will move by the aforementioned 0.6 mm. The fine handle 92 has a vertical movement amount of the center point α of 0.02 m<20 μm per rotation. Fine handle 92
is provided with a fine adjustment scale 93, and this fine adjustment scale 93 can be scaled on the order of 100 minutes/μm. In the embodiment described above, the gear ratio of the worm gear 95.97 is /:60. Although the X dimension is 0.3 mm, there is no need to stick to this, and it is possible to use other values.
The application range of fine movement feed is wide-ranging.

Since the fine movement feeding device of the present invention has the above-described configuration, it has the following advantages compared to the conventional fine movement feeding device.

m It is possible to perform fine movement with very small dimensions (side support 7 μm).

(2) Fine adjustment does not require precision pinch screws, so it is easy to process and can be manufactured at low cost. (3) Since fine adjustment screws are not used, the allowable load for fine adjustment is particularly small. Since it can withstand a considerable load without causing damage, there is no need to limit the objects to be processed or measured.

(4) Since /JX thin screws are not used, screw k
There is no play (gap) when fitting due to twisting, and there is no wear due to screw rotation, so errors in assembly are small.

[Brief explanation of the drawing]

FIG. 1 is a diagram showing the principle of a fine movement feeder as an example of the present invention, FIG. 1 is a diagram showing the principle of a fine movement feeder as another embodiment of the invention, and FIG. FIG. 9 shows a fine movement feeder as another embodiment of the present invention.
The figure shows still another embodiment of the present invention, Figure S is a schematic cross-sectional front view showing an optical fiber end face polishing device using the fine movement feeder of the present invention, and Figure 6 is Figure S. FIG. 1...B, x unit, 2...Movable head, 3...Fine adjustment cam shaft, 4...Fine cam, 5... ...This metal fitting, 6... Spring.

Claims (4)

[Claims] (1) A movable head that is shifted in one direction on the pace table, a fine adjustment cam shaft that is provided to rotate on the pace table, and a circular fine adjustment cam that can rotate together with the fine adjustment cam shaft. The center of the fine adjustment cam is eccentric from the center of rotation of the adjustment cam, and the front surface of the front fine adjustment cam is in a state facing the front displacement force with respect to the movable head. A fine movement feeding device for a precision instrument, wherein the movable head moves slightly against the shifting force by the action of the fine adjustment cam as the fine adjustment cam rotates. (2) 11 above! A fine movement feeder for a precision instrument according to claim (1), wherein the peripheral surface of the adjustment cam is in contact with the movable head through sliding contact with a flat contact tool fixed to the movable head. . (3) The peripheral surface of the front r fine adjustment cam is in contact with the front Mr' movable head through sliding contact with a goal-shaped or roll-shaped member rotatably provided within the fixture of the movable head. A fine movement feeder for a precision instrument according to claim 11. (4) The front r fine adjustment camshaft is rotated by a dial for fine adjustment via a speed reduction mechanism. .