JPS5823556Y2 - Workpiece positioning device - Google Patents

Description

[Detailed Description of the Invention] The present invention relates to a positioning device for positioning a workpiece at a processing position.

Generally, when processing a workpiece after moving it to the processing position and positioning it, good processing cannot be achieved unless the workpiece is positioned within a predetermined error range. Especially when processing automatically, positioning Errors appear noticeably in the machining results.

As shown in FIG. 1, this type of conventional positioning device includes moving members 1/, 1/ which are restrained by guide members 2', 2' and are movable in the 1-2 force direction. A receiver 3 is attached to the tip of the moving member via a plate-like member.

A workpiece 8 is held in the O holder 3, and the workpiece 8 is moved in the YI and Y2 directions by a hydraulic cylinder having a cylinder rod connected to a plate-like member. .

To position the workpiece at the processing position, a moving member 1';
1' is displaced by a distance. In this case, the movement of the cylinder rod of the hydraulic cylinder is transmitted to the workpiece 11, so if the protrusion length of the cylinder changes by, for example, JL, the amount of change JI.

Therefore, the position of the workpiece also changes.

For example, when positioning a workpiece by stopping a moving member using a stopper in the middle of a cylinder stroke, the deviation AL of the set position of the stopper becomes the deviation of the workpiece that falls into the 11 processing positions. In addition, when positioning the workpiece at the protruding end position of the cylinder rod, when the piston of the fluid pressure operated cylinder or the so-called rod cover in contact with the piston wears out, the amount of wear JL increases. 11 There was a drawback that appeared due to misalignment of the workpiece.

Furthermore, if a force is applied to the workpiece and the moving member in the Y2 direction (direction toward the cylinder side) against the machining position, the pressing force of the fluid pressure operated cylinder in the Y1 direction is increased to withstand this force. The larger the force acting on the workpiece, the more it is necessary to use a larger hydraulic cylinder, which is uneconomical.

Further, in the apparatus shown in FIG. 1, when the moving member is stopped by a stopper in the middle of the stroke of the cylinder to position the workpiece, for example, a double lock nut N screwed onto a screw at the end of the moving member 11, In order to prevent the lock nut from turning, a knock pin (not shown in FIG. 1) is inserted into a hole provided in the nut and the moving member.

) are used, and the moving member 1' is provided with holes arranged at predetermined intervals in the direction of the axial force, into which the knock pins are inserted.

In this case, since the amount of movement of the cylinder and the amount of movement of the moving member are equal, in order to finely adjust the position of the workpiece, it is necessary to reduce the interval between the holes for engaging the knock pins.

However, if the distance between the holes is too small, the mechanical strength of the moving member will decrease, and in extreme cases, adjacent holes will overlap. In some cases, it was difficult to make the accuracy of the calculation sufficiently high.

An object of the present invention is to provide a workpiece positioning device that eliminates the above-mentioned conventional drawbacks.

The present invention will be explained in detail below with reference to the illustrated embodiments. In Figs. A receiver 3 that comes into contact with the workpiece 8 is disposed at the end in the Y1 direction, and a contact portion 4 made of, for example, a rotatable roller is disposed at the Y2 force direction.

Reference numeral 5 denotes a cam which is restrained by a guide member 6 and is movable in a direction substantially perpendicular to the direction of movement of the movable member, that is, in the X1-X2 direction.As shown in FIG. For example, a steep slope 501 forming an angle α1 with respect to the line formed continuously.

Reference numeral 7 denotes a drive device, such as a hydraulic cylinder, for moving the cam 5 in the Xl-X2 force direction.

In this embodiment, a hydraulic cylinder 701 is used as this drive device.
is used, and its cylinder rod 702 is connected to the cam 5.

In the above embodiment, when moving the workpiece 8 in the ¥1 force direction and positioning it, the hydraulic cylinder 701 is operated so that the cylinder rod 702 is retracted, and the cam 5 is positioned at the end position in the X2 direction. I'll keep it.

After the workpiece 8 is placed on or above the receiver 3 in this state, the hydraulic cylinder 701 is operated to cause the cylinder rod 702 to protrude.

As a result, the cam 5 moves in the X direction, and the moving member 1 moves together with the contact portion 4 in the Y1 direction.

In this case, the height of the steep slope 501 in the Y and -Y directions is set so that the workpiece 8 is transferred to position 1, which is slightly in front of the processing position, and the height of the gentle slope 502 is set so that the workpiece 8 is transferred to position 1, which is slightly in front of the processing position. The height in the Y and -Y directions is set so that the workpiece transferred at the front position 1 is further transferred to the processing position 1.

Therefore, for example, when positioning the workpiece 8 at a position where the movable member has been moved a distance in the Y direction, the contact portion 4 first contacts the steep slope 501 while the movable member 1 is moved a distance in the Y direction. move by a distance L-JL, which is slightly smaller than
Subsequently, the movable member 1 is moved while the contact portion 4 is in contact with the gentle slope 502.
moves by AL in the direction of the force.

With this configuration, the workpiece can be positioned quickly and accurately.

That is, in the above device, as shown in FIG. 5, in the section where the contact part 4 is in contact with the steep slope 501 of the cam 5, when the cam 5 moves by a unit distance critical it in the X1 direction, the contact part 4 moves in the ¥1 direction by AL1=lt-tanα1.

In the section where the contact part 4 is in contact with the gentle slope 502, when the cam 5 moves in the X1 direction by a unit distance At, the contact part 4 moves in the Y1 direction A L2 = l l ・tan a
, only move.

Here, for example, if α1 = 45° and α2 = 5°, the above IL and AL2 are respectively JLI = jit-ta
r145°=At, and yL2=0.087·At in Jz−tan5°.

That is, while the workpiece is being transferred at position 1, which is just before positioning, the transfer is performed quickly due to the steep slope, and in the section just before positioning, the moving member 1 is
Since the amount of movement JL2 becomes sufficiently small, positioning can be performed accurately.

For example, when α2-5° is set as described above, even if the cylinder rod 702 deviates by lt=lOmm in the X1 direction, the amount of movement of the workpiece 8 in the Y direction is JL2K0.
It is only 087 x 100.87 mm.

Therefore, when the drive device 7 is a hydraulic cylinder 701, a signal for switching the 3-position solenoid valve is generated depending on the position of the check valve, the 3-position solenoid valve, and the cam 5, for example, without providing a mechanical stopper. cam 5 automatically by a limit switch that closes the check valve, a deceleration valve that seals the check valve, a two-position solenoid valve, etc.
The workpiece 8 can be positioned by stopping the position of the workpiece 8.

Furthermore, even if the hydraulic cylinder 7010 parts wear out and the cylinder rod 702 moves in the X1 force direction, the position of the workpiece 80 hardly changes.

Since the movement of the cylinder rod 702 due to wear is only a matter of effort at most, it hardly affects the positional fluctuation of the workpiece 8 according to the above relational expression.

When using a pneumatic cylinder as the drive device 7, a stopper is used to determine the position of the cam 5.
In this case, when the position of the workpiece 8 is changed from a predetermined position by, for example, two steps, the variation distance of the cam 5 in the Since the mounting holes do not overlap with adjacent holes, the position of the workpiece 8 can be changed without any problem.

In FIG. 6, a moving member 1, a guide member 2, and a contact portion 4 are shown.
When the friction angle between the cam 5 and the cam 5 and the guide member 6 is λ1 to λ3, and the force in the Y2 direction acting on the moving member 1 is Q, the force F that tries to press the cam 5 in the X2 direction is: It is.

Here, the kinetic friction coefficient μi and the friction angle λi are mechanically expressed as μ1−tanλi, and the value of μi, that is, the value of μ and μ2, can be set depending on the sliding condition and material. be.

Now μm=tanλ,=0.15. μ2=tanλ20
．． 001, if a2=5°, then λ, two tan-1
8° 30' in 0,15, λ2=jan'0.0
From 01 Cow O, FQltan (8°30'+O+5°)
Medium 0.24-Q.

That is, when a force in the Y2 direction of Qi is applied to the moving member 1 via the workpiece 8, the pressing force F of the driving device 7 in X17j is
may have a value of approximately Q/4, and therefore the drive device 7 can be made smaller and cheaper than the conventional drive device 7 shown in FIG.

Note that when the cylinder rod 702 is retracted in the X2 direction, the moving member 1 moves in the Y2 direction together with the contact portion 4.

In this case, for example, when the Y2 direction is the gravity direction,
Although the movable member 1 moves in the Y2 direction together with the contact portion 4 due to its own weight, a spring member, for example, is arranged so as to forcibly bias the movable member 1 in the Y2 direction regardless of the difference between the Y2 direction and the direction of gravity. The power he has is good.

Furthermore, by providing anti-friction members, especially bearings, on the sliding parts of the moving member 1 and the guide member 2, the cam 5 and the guide member 6, etc., the pressing force of the hydraulic cylinder 701 can be reduced, and therefore the hydraulic cylinder 701 can be made smaller. And it can be made inexpensive.

Further, as the drive device 7, a fluid pressure drive motor or a combination of an electric motor and a screw mechanism can be used.

If the contact part 4 is constituted by a rotatable roll, the movement of the contact part 4 with respect to the cam 5 will be performed smoothly, and the kinetic friction between the contact part 4 and the cam 5 or the movable member 1 and the contact part 4 will be reduced. Since the coefficient is small, even if a force Q in the direction of the ¥2 force is applied to the moving member 1 via the workpiece 8 during positioning, the cam 5 will not be
The force F pressing in the direction becomes smaller, and therefore, if the driving force of the drive device for the workpiece 8 is larger than the force F, the workpiece 8 cannot be positioned even if the force Q in the Y27i direction acts during positioning as described above. status is not affected.

As a result, the driving force of the drive device for the workpiece 8 can be reduced, so the device can be manufactured compactly and at low cost.

7 to 9 show another embodiment of the present invention, in which the movable member 1 is provided with two substantially cylindrical guide bars ioi, 1oi, and these guide bars It is guided by guide members 2, 2.

The guide members 2, 2 have openings on faces facing each other in the illustrated Zl-X2 direction, and the guide rods ioi, 2 are inserted through the openings.
Both guide rods are connected by a connecting member 102 connected to the middle portion of the IOT.

The contact portion 4 with the cam 5 is supported by the connecting member 102.

With this configuration, the dimensions of the positioning device in the Y and -Y2 force directions can be reduced, and the device can be configured compactly.

Further, in this embodiment, the steep slope 501 of the cam 5 is
A second gentle slope 5 that extends in the X1 direction continuously from the end in one direction.
03 is provided.

By providing the second gentle slope in this way, the contact portion 4 and the cam 5
Since the static frictional force between the cam 5 and the movable member 1 can be reduced, the movement between the cam 5 and the moving member 1 can be smoothly performed.

FIG. 10 shows still another embodiment of the present invention. In this embodiment, the contact portion 4 is made of a block material that makes surface contact with the cam surface, and the end portion of the contact portion in the Y2 direction is Contact surfaces 401 and 402 having slopes having the same slope angle as the steep slope 501 and the gentle slope 502 of the cam 5 are provided.

When the contact portion 4 and the cam 5 make surface contact in this way, even if a force in the Y27i direction is applied to the moving member 1, the contact portion 4 and the cam 5
Since the stress on the contact surface with the button is alleviated, the life of the contact portion 4 and the cam 5 can be extended.

In this case, the friction angles between the moving member 1 and the guide member 20, between the moving member 4 and the cam 50, and between the cam 5 and the guide member 60 are set to λ1. λ2 and λ3, ¥27 acting on moving member 1
jIf the force is Q, then the force F that tries to press the cam 5 in the Y2 direction is expressed as shown above.

Here, λ1-λ2=λ3, and μm=tan
λ1=0.15 (where μm is the coefficient of kinetic friction), α2-5
If it is °, then λ1-jan' 0.15:8°30
'From F=Q-tan (17°+5°) 0.4-Q
becomes.

That is, when a force Q in the direction of the ¥2 force acts on the movable member 1 via the workpiece 8, the driving force for pressing the cam 5 in the X1 direction may be 40% of the value of Q.

Therefore, compared to the conventional device shown in FIG. 1, the drive device can be made smaller, the device can be constructed more compactly, and it can be manufactured at a lower cost.

Of course, the value of F is largely influenced by the values of λ to λ3, but the value of F can be made as small as possible by providing anti-friction members, especially bearings, at each sliding part. .

FIG. 11 is a schematic diagram showing still another embodiment of the present invention, and in this embodiment, by moving the cam 5 in the X2 direction, the abutment member 4 is moved in the Y2 force direction for positioning. It is configured.

Note that when positioning the workpiece 8 by moving the moving member 1 in the Y1 direction as shown in FIG. 2, FIG. 7, or FIG. It is possible to configure a so-called clamp button and positioning position, which is arranged on the ¥1 force direction side of the workpiece 8 and restrains the workpiece 8 with the corresponding material and the receiver 3.

In this case, when the driving force of the drive device 7 that drives the cam 5 in the X1 direction is F, the force Q that drives the moving member 1 in the ¥1 force direction is F-shaped 0.24Q or F=:
=0.4Q, so Q=4・F or Q
'=2.5·F, and the clamping force can be increased.

Further, since the cam 5 is provided with a steep slope for moving the workpiece 8 and a gentle slope for positioning the workpiece 8, the cam 50 is used to move the moving member 1 and the workpiece 8.
Positioning buttons and clamps can be performed with relatively short strokes.

In the embodiment shown in FIG. 10, the contact portion 4 has a contact surface 40.
1 and 402, but in this case, the contact portion 4 has at least a contact surface 402 corresponding to the gentle slope 502 of the cam 5.
It is sufficient if it is provided.

Although various preferred embodiments of the present invention have been shown above, the present invention is not limited to these embodiments.
Various modifications can be made by appropriately combining the parts of the above embodiments or replacing each part with an equivalent member.

As described above, according to the present invention, a cam that moves linearly and a moving member that comes into contact with the cam and moves in a direction substantially perpendicular to the direction of the moving force of the cam are provided, and the cam surface of the cam has at least a steep slope and a gentle slope. By providing a slope, the steep slope is used when the workpiece moves, and the gentle slope is used when positioning the workpiece, so the movement stroke of the cam can be relatively short, and the necessary drive This is industrially advantageous because the driving force of the device is small and positioning can be performed with high precision.

[Brief explanation of the drawing]

Fig. 1 is a partially sectional front view showing a conventional example, Fig. 2 is a front sectional view showing an embodiment of the present invention, and Figs. 3 and 4 are lines ■-■ and IV-IV in Fig. 2, respectively. 5 and 6 are explanatory views of the operation of the device shown in FIG. 2, FIG. 7 is a front sectional view showing another embodiment of the present invention, and FIG. 8 is a button and a button 9.
The figures are sectional views taken along lines 1--2 and IX--IX in FIG. 7, respectively, and FIGS. 10 and 11 are schematic front views showing essential parts of other embodiments of the present invention, respectively. 1...Moving member, 2...Guide member,
4... Contact portion, 5... Cam, 501.
... Steep slope, 502 ... Gentle slope, 503 ... Second gentle slope, 7 ... Drive device, 8 ... Workpiece .

Claims (3)

[Scope of utility model registration request] (1) A cam having a cam surface having at least a gentle slope and a steep slope, the cam being moved linearly by a drive device, and a contact portion with the cam surface, the direction of the movement force of the cam as the cam moves. A positioning device for a workpiece, comprising: a moving member guided by a guide member so as to move linearly in a substantially perpendicular direction, and a workpiece is transferred to a processing position by the moving member. (2) The workpiece positioning device according to claim 1, wherein the contact portion is a rotatable roll. (3) The workpiece positioning device according to claim 1, wherein the abutting portion has at least an abutting surface having an inclination substantially the same as a gentle incline of the cam.