JP2952537B2 - Roll feeder release device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a release device for a roll feeder, and more particularly to a releasable operation having a remarkably high speed.

[0002]

2. Description of the Related Art There is known a roll feeder which has an upper roll and a lower roll, and feeds a sheet material in a predetermined direction while being held between both rolls. When this roll feeder is used as a material supply device for a press, it is necessary to equip a release device. That is, the release device is provided with the pilot pin (2) in the guide hole of the plate material fed into the press.
When the position of the plate is adjusted by inserting [see FIG. 8], the upper roll (lower roll) is released (released) from the lower roll (upper roll) to secure the degree of freedom in the feeding direction of the plate. Means.

A typical configuration of such a release device (60P) is shown in FIGS. In FIG. 7, the roll feeder 10P is a one-roll drive system including a lower roll 21P on a rotary drive side and an upper roll 11P on a rotatable side. The release device 60P includes a lever 68P that rotatably holds the upper roll 11P at its tip and swings about a fulcrum Q, and a cylinder device 82P connected to the lever 68P via a piston rod 85P. Therefore, when the cylinder device 82P is driven to project the piston rod 85P, a touch (clamp) operation of pressing the upper roll 11P against the lower roll 21P is performed. Conversely, a release operation can be performed by retracting the piston rod 85P.

In addition, such a release device 60P can follow even if the thickness of the plate material W to be applied changes, so that it also serves as a thickness-corresponding position adjusting device.
For this reason, the full stroke of the cylinder device 82P is
In addition to moving the upper roll 11P by the release amount,
It is a large stroke that can be moved by the maximum thickness of the plate material W. The cylinder device 82P is switched between a release operation and a touch operation by an electromagnetic switching valve (not shown). It is automatically switched by a control device (not shown).

On the other hand, a release device 60P shown in FIG.
It comprises a toggle mechanism 61P and release drive means 81 (cylinder device 82P and electromagnetic switching valve 87P), and is mounted on the rotatable lower roll 21P of the roll feeder 10P of a single roll drive system. In addition, 1 is a press and 2 is a pilot pin.

The toggle mechanism 61P has a structure in which a link 63P holding the lower roller 21P and another link 64P, one end of which is rotatably supported by a pin 64PS, are connected by a joint (top) 62P. Therefore, the top 62P can be moved rightward in the figure to perform a touch operation indicated by a solid arrow, and moved leftward to perform a release operation indicated by a dotted arrow. Also in this case, the full stroke of the lower roll 21P is equal to or larger than the maximum thickness of the plate material W to be applied. This is because the thickness adjusting position adjusting device is also used.

Therefore, the solenoid 87PS of the electromagnetic switching valve 87P is energized (non-excited) and the position AP (C
P) to supply the pressurized air P0 to the one chamber 83T (the other chamber 83L) in the cylinder 83P.
Since P, that is, the piston rod 85P moves rightward (leftward), a touch operation (release operation) can be performed. It can follow changes in the thickness of the plate material W. Note that the position BP is neutral.

[0008]

However, in any of the conventional release devices (FIGS. 7 and 8), there are factors for limiting the speeding-up as described in the following [-].
The release operation cannot be performed more than 0 to 250 times.

When the cylinder device 82P performs a stroke operation, the upper roll 11P of FIG. 7 and the lower roll 21 of FIG.
In both cases, P moves continuously up and down as shown in FIG. Incidentally, the release operation is performed with the roll separated from the plate material W when the crank angle is 180 ± α degrees. On the other hand, basically, at other crank angles (for example, around 220 to 360 to 170 degrees), the touch operation, that is, the clamp operation must be performed in preparation for the feed. Thus, the cylinder device 86P, the electromagnetic switching valve 8
It is very difficult to take the timing of switching the solenoid 87PS of the electromagnetic switching valve 87P in anticipation of the 7P operation delay as the press speed increases.

[0010] The cylinder device 82P has a one-side chamber 83T.
The exhaust action of the air in the (other chamber 83L) proceeds, and the air supply action of the other chamber 83L (one chamber 83T) is promoted accordingly.
Is a structure that can perform a stroke operation. Therefore, the operation time is long. As a measure to shorten the operation time, it is conceivable to increase the supply air pressure. However, in this measure, since a large pressing force is applied to the plate material W, it is not practical from the viewpoint that it cannot be applied to a weak plate material made of an aluminum alloy or the like. In addition, the release time cannot be reduced in proportion to the increase in the air pressure, and the equipment cost is significantly increased.

The structure of the electromagnetic switching valve 87P is such that when the solenoid 87PS is excited, the movable core moves to open the control air passage. Then, the sub-spool guides the control air to the switching air passage and the main chamber against the urging force of the spring. This allows
The main spool moves to the position (AP, BP, C
In general, it is configured to switch P). That is, the double spool type air flow is more complicated than the cylinder device 82P. Accordingly, when the solenoid 87PS is excited and the movable core is displaced, a large time lag (for example, 1 / 50Sec) occurs until the sub-spool opens the switching air passage, and the main spool is moved to a predetermined position by the switching air. Time lag (for example, 3 / 100Se)
c) is inevitable. Further, since there is an increase in frictional force and the like, the time lag is further increased.

Due to the above factors, the roll feeder 10
It has been difficult in practice to reduce the release time of P to, for example, 2/100 sec or less. Therefore,
The release device (60P) employed in a high-speed press of 200 to 250 SPM or more is formed of a so-called mechanical release mechanism that is synchronously driven by a crankshaft of the press via a cam mechanism, a link mechanism, a gear mechanism, and the like. It is a fact. However, in this release mechanism, the structure is complicated and large, and the cost is very high. In addition, there are many operational obstacles in that the release operation or the like cannot be confirmed while the press is stopped.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a roll feeder release device capable of achieving a high-speed release operation while ensuring stable and accurate supply of a plate material.

[0014]

According to the present invention, there is provided a release device for a roll feeder, wherein one of an upper roll (11) and a lower roll (21) for supplying a sheet material in a predetermined direction while rotating and holding the roll material is timely. In a release device of a roll feeder (10) that moves up and down by a predetermined release amount, one of the upper roll and the lower roll is released along a vertical axis (Z1) toward the other roll. A first toggle mechanism (61) for touch operation and a top (72) vertically moved by a cylinder device (82), and the top (62) of the first toggle mechanism is horizontally moved through one link (73). A second toggle mechanism (71) for reciprocating in a direction and a pair of links (63, 64) forming the first toggle mechanism so as to be linear along the vertical axis. Urging means (95) for applying a constant urging force to the top (62) of the cylinder (82), and the horizontal direction of the top (62) forming the first toggle mechanism before the full stroke in the touch operation direction of the cylinder device (82). The cylinder device is connected to a stopper (97T) for restraining the position and to the fixed end side of the other link (74) forming the second toggle mechanism, and the top (62) of the first toggle mechanism is restrained in position by the stopper. Storing means (91) formed to store the kinetic energy in the touch operation direction of (82) and to be able to release the energy to the top (72) of the second toggle mechanism as the urging force in the release operation direction at the start of the release operation. And a configuration comprising:

[0015]

According to the present invention having the above construction, the cylinder device (8
2), the top (72) of the second toggle mechanism (71) is raised, for example. Then, the one link (73) presses the top (62) of the first toggle mechanism (61) horizontally and rearward, so that the two links (63, 64) are connected to the vertical axis (Z).
It moves so as to be linear along 1). At this time, the top (6
2) a biasing means (9) for supporting its own weight such as a roll.
Since 5) is connected, it can operate smoothly even with relatively light power.

The top (62) has a stopper (97).
When the position is restricted by T), the roll (21) is
And a clamp is made with a predetermined pressing force. Therefore, even if high-pressure air is applied to the cylinder device (82), the pressing force can be kept constant. That is, high-speed operation is possible. Further, there is no problem even if the stroke of the cylinder device (82) is made larger than the release amount, and the control thereof can be simplified.

Therefore, the cylinder device (82)
Rises in the direction of the touch operation, the first toggle mechanism (6
Since the top (62) of 1) is positionally restricted, its kinetic energy is stored in the energy storage means (91) connected to the fixed end of the other link (74) forming the second toggle mechanism (71).
Is stored in

Thus, when the cylinder device (82) reaches a full stroke and then descends, the top (62) of the first toggle mechanism (61) separates from the stopper (97T), so that the roll (21) is placed on the plate (W). ) And release operation is possible. At this time, the energy stored in the energy storage means (91) is released to the cylinder device (82) via the other link (74) and the top (72) in the release operation direction. Therefore, a high-speed release operation can be performed at a remarkably high speed, and for example, a release operation of 1,000 times or more per minute can be achieved.

[0019]

Embodiments of the present invention will be described below with reference to the drawings. This release device 60 is, as shown in FIGS.
A double toggle mechanism (61, 71), an urging means 95 connected to the first toggle mechanism 61, and a second toggle mechanism 7
1 and a release driving means 81 for applying a release operation force via the top 72 of the second toggle mechanism 71 to make the pressing force of the lower roll 21 constant.
The speed is increased by enlarging the full stroke of the cylinder device 82 and increasing the supply air pressure, the switching speed of the release driving means 81 is increased, and the release operation is accelerated by releasing the stored energy.
It is formed so that zero or more rapid high-speed release operations can be performed.

In this embodiment, both rolls (11,
21) A high-precision feeding of the plate material W is made possible by adopting a driving system and a configuration in which the driving device 31 can eliminate the influence of the gear backlash.

Further, the upper roll 11 is connected to the thickness-adjusting position adjusting device 50 so that the thickness follow-up adjustment and the main release operation can be performed separately and independently, thereby minimizing the release amount. It is configured so that a higher-speed release operation can be performed.

First, the roll feeder 1 in the present embodiment
0 will be mainly described with reference to FIG. In FIG. 3, the upper roll 11 is rotatably supported by an upper slider 15 mounted on the machine frame 5 so as to be vertically movable, and an upper driven bevel gear 12 is integrally attached to a left end thereof. That is, the upper driven bevel gear 12 and the upper roll 11 are considered to be an integral body that rotates synchronously. Similarly, the lower roll 21
3 and 4, a lower driven bevel gear 22 is integrally mounted, and is rotatably supported by a lower slider 25 as a whole. The lower slider 25 is also mounted on the machine frame 5 so as to be vertically movable. Here, it is understood that the upper roll 11 and the lower roll 21 can move up and down independently of each other along the vertical axis Z1.

Incidentally, between the sliders 15 and 25, springs 16 and 26 for balance are interposed, and both rolls 11 and 25 are provided.
21 is biased so as to be separated in the vertical direction. The spring 16 is stronger than the urging force of the spring 26 so as to retain the weight of the upper driven bevel gear 12 and the like.

Next, the driving device 31 includes a servo motor 32 as a rotary driving source, a driving shaft 34 and the driving shaft 3 shown in FIG.
The upper and lower drive bevel gears 35, 45, etc., which are fitted and mounted on the roller 4, can rotate both the rollers 11, 21 synchronously.

That is, the upper drive bevel gear 35 is
4 is mounted so as to be synchronously rotatable with the upper spline 34U engraved on the drive shaft 4, and is mounted so as to be movable relative to the drive shaft 34 in the vertical direction. Reference numeral 36 denotes a shoe, and the driving shaft 3
4 is rotatably supported on the upper slider 15 and allows the upper drive bevel gear 35 to move up and down with respect to the drive shaft 34. Only the clearance C shown in FIG. 3 is allowed.

The upper drive bevel gear 35 has a drive shaft 3
4 and a spring 37 interposed between the flange 37F fixed to the
3, it is pulled downward in FIG. 3, that is, in the direction of the flange body 37F. This spring 37 forms the upper biasing means. That is, the upper driven bevel gear 35 is the upper driven bevel gear 1
2 is always urged to engage in an appropriate state. Therefore, even if the upper roll 11 moves up and down along the vertical axis Z1 together with the upper slider 15, the upper bevel gear mechanism (1
The backlash in (2, 35) is constant and their mesh does not come off.

On the other hand, the lower drive bevel gear 45 is fitted to the drive shaft 34 via the lower spline 34L so as to be synchronously rotatable, and is pulled in the direction of the flange 47F by a spring 47 forming a lower urging means. I have. Therefore, even if the lower roll 21 is moved up and down along the vertical axis Z1 together with the lower slider 25, the backlash of the lower bevel gear mechanism (22, 45) is constant and their mesh does not come off. The lower end of the shoe 46 interposed between the lower slider 25 and the drive shaft 34 is fixed to a bracket 48 integrated with the drive shaft 34.

That is, in this embodiment, the upper drive bevel gear 35 is mounted on the drive shaft 34 via the upper spline 34U so as to be relatively movable in the up-down direction.
Although the vertical movement of the (upper slider 15) is allowed, the lower drive bevel gear 45 is formed so as to move up and down together with the drive shaft 34 connected via the shoe 46 and the bracket 48. For this purpose, a spline 34D provided at the lower end of the drive shaft 34 is inserted and connected to a spline member 33 integral with the rotation shaft of the servomotor 32.

Therefore, even if the lower roll 21 is moved up and down together with the lower slider 25 and the drive shaft 34, the torque of the servo motor 32 can be transmitted to the drive shaft 34. That is,
The rotation of the drive shaft 34 is transmitted to the upper roll 11 via the upper bevel gear mechanism (35, 12) and the lower bevel gear mechanism (45, 22).
Through the lower roll 21.

Here, the bevel gear mechanism (35, 1)
The relationship between 2) and the lower bevel gear mechanism (45, 22) is mechanically exactly the same. However, the upper roll 11 and the lower roll 2
The rotation transmitted to the rotation direction 1 is reversed due to the difference in the direction of the meshing position. Therefore, the bevel gear mechanism (35, 1
2) Mechanical backlash and mechanical bevel gear mechanism (4
Even if there is a mechanical backlash of 5,22),
The rotation of the drive shaft 34 can be simultaneously transmitted to the upper roll 11 and the lower roll 21.

That is, the effect of backlash is removed,
Since the two rolls 11 and 21 can be simultaneously rotated and started up and can be rotated synchronously, the plate material W can be driven from both sides and fed to the press with high accuracy. In addition, since the two-roll drive system is used, the pressing force of the upper and lower rolls 11 and 21 can be reduced, so that a soft plate material W such as an aluminum alloy can be accurately fed.

Next, a thickness-adjusting position adjusting device 50 is a means for adjusting the gap between the two rollers 11 and 21 in accordance with the thickness of the plate material W.
1 (axis Hh) is moved up and down within the maximum thickness (△) of the plate material W.

That is, the position adjusting device 50 corresponding to the thickness
As shown in FIG. 3, the screw shaft 55 is rotated via the shaft 52, the worm screw 53 and the worm wheel 54 by rotating the handle 51. Then, the screw shaft 55 moves up and down with respect to the nut member 56 fixed to the machine frame 5, so that the upper slider 15 can move up and down.

The vertical movement stroke of the upper slider 15, ie, the upper roll 11, by the thickness-corresponding position adjusting device 50 is equal to or larger than the maximum thickness (△) of the plate material W to be applied. Release device like (60P)
Is not used, so that the vertical movement stroke can be selected with a sufficient margin. That is, the applicability is wide.

The upper roll 11 is driven by the drive shaft 34 because the backlash of the upper bevel gear mechanism (12, 35) is constant and the mesh does not come off, no matter where the height of the upper roll 11 is adjusted. Is always smoothly rotated. The amount of vertical movement of the upper roll 11 (upper slider 15) is not particularly limited, but in this embodiment, a clearance C (for example, between the upper end flange of the drive shaft 34 and the upper end surface of the shoe 36 shown in FIG. , 5 mm).

On the other hand, the release device 60 performs the release operation by moving the lower roll 21 (axis Hl) of FIG. 3 up and down, and operates independently and independently of the position adjusting device 50 corresponding to the thickness. Therefore, the release amount can be determined extremely small, and in the case of this embodiment, the release amount H shown in FIGS.
c (for example, 0.5 mm). First, the release operation is accelerated by minimizing the release amount. This can be easily understood by comparing with a conventional example in which the value of the clearance C (5 mm) or more is a release amount.

As shown in FIGS. 1 and 2, the release device 60 comprises a double toggle mechanism (61, 71), release drive means 81, storage means 91, and urging means 95. In FIG. 1, the first toggle mechanism 61 joins (links) one link 63 whose upper end is rotatably supported by the lower slider 25 with the pin 63S and the other link 64 whose lower end is rotatably supported by the machine frame 5 with the pin 64S. The lower roll 21 is configured to be touched (released) by moving the top 62 rightward (leftward). That is, when both links 63, 64 are linear along the vertical axis Z1, the lower roll 21 can touch the lower surface of the plate material W, and the upper and lower rolls 11, 12 can be touched.
1, the plate material W can be clamped.

Incidentally, the weight of the lower roll 21, the lower slider 25, and the like is added to the first toggle mechanism 61 (one link 63). Therefore, the urging means 95 is connected to the top 62 so as to cancel the weight, that is, the two links 63 and 6.
A biasing force in the direction B is applied to make 4 a straight line. As shown in FIGS. 1 and 2, the urging means 95 includes a cylindrical body 97 whose base end 97A is rotatably attached to the machine frame 5 with a pin 97S.
And a connecting member 98 capable of being displaced in the axial direction in the cylindrical body 97, and a spring 96.

The spring 96 is provided between the cylindrical body 97 and the rod 98B, and is interposed between the inner end surface of the cylindrical body and the flange 98C.
It is biased in the direction of arrow B shown in FIG. Therefore, since the head 98A of the connecting member 98 is rotationally connected to the top 62, both links 63 and 64 are urged to be linear.

Here, the outer end surface (97T) of the cylindrical body 97
Is a stopper 97T for restraining the horizontal position of the top 62.
To form The stopper 97T is connected to both links 63,
When 64 becomes linear, that is, when the lower roll 21 is at a predetermined position (touch) with respect to the upper roll 11,
The first toggle mechanism 61 (top 62) via the head 98A.
The position of. Therefore, the top 62 is
When the position is restricted at 7T, it can be considered that the entire first toggle mechanism 61 forms a fixed end with respect to the second toggle mechanism 71.

Next, the second toggle mechanism 71 has a one-side link 7 whose right end (upper end in FIG. 2) in FIG.
And a third link 74 rotatably supported by a power storage means 91 (described later in detail) with a pin 74S at the left end to a joint (top) 72. The cylinder forms a part of the release driving means 81. The top 82 is moved up and down by the device 82 to apply a horizontal force to the first toggle mechanism 61 (62).

The first object of the double toggle mechanism (61, 71) comprising the first and second toggle mechanisms is as follows.
This is because the release amount is made small with respect to the large stroke momentum of the cylinder device 82 and the touch operation can be maintained for a long time. The second object is to provide the urging means 9
5 and the storage means 91 can be incorporated.

That is, with respect to the first object, the relationship between the amount of vertical movement of the top 72 of the second toggle mechanism 71 and the amount of horizontal movement of the top 62 of the first toggle mechanism 61 is as shown in FIG. Become. Also, the relationship between the horizontal movement amount of the top 62 and the vertical movement amount of the lower slider 25, that is, the lower roll 21 (pin 63S) is as shown in FIG.

Therefore, the vertical stroke Hc of the lower roll 21 (63S) can be made much smaller than the stroke (trajectories 1, 2,..., 8) of the piston rod 85 (top 72), and is shown in FIG. As a result, the roll touch can be performed only by Hg in the vertical full stroke Hc. For example, H
c: Hg = 2.6: 0.7. This means that the release operation timing of the cylinder device 82 can be set very easily.

Further, the vertical stroke of the cylinder device 82 may be increased, and the stroke may be rough, and it is not necessary to stop the cylinder device 82 at a predetermined position accurately.
This is directly linked to high-speed driving. Furthermore, since the stopper 97T can be introduced, the roll touch operation for feeding the plate material W can be performed stably and accurately. Further, the urging force of the urging means 95 does not fluctuate due to the action of the stopper 97T, and the pressing force of the lower roll 21 against the plate material W does not change. Moreover, even if high-pressure air is applied to the cylinder device 82 to perform a high-speed stroke operation, it is possible to prevent the pressing force from becoming excessive. This is because the pressing force is determined by the strength of the spring 92 described later in detail.

If the double toggle mechanism (61, 71) is used, as shown in FIG. 1, the stroke direction of the cylinder device 82 is changed to the axis Z1 in the release operation direction of the lower roll 21.
And a vertical axis Z2 parallel to Therefore, since the direction is the same, a smooth release operation can be guaranteed.

However, in view of the first object, the movement of the cylinder device 82 in the touch operation direction (the direction from the bottom to the top in FIG. 1) after the top 62 of the first toggle mechanism 61 is restrained by the stopper 97T. Energy is wasted. Here, the storage means 91 as the second purpose
And effectively works to achieve the original purpose of speeding up the release operation.

That is, as shown in FIGS. 1 and 2, the energy storage means 91 includes a connecting member 93, a guide portion 94 for slidingly guiding the rod portion 93B, a rod portion 93B and the guide portion 9
4 and its head, that is, the pin 74S
And a spring 92 biased in the direction. Therefore, in a normal state, the spring 92 urges the pin 74S rightward (R direction) in FIG. 1, and the distance of the pin 74S from the fixed end of the pin 64S in FIG. Rest in position. That is, it functions as forming a fixed end of the second toggle mechanism 71 (the other link 74).

Here, when the cylinder device 82 rises (touch operation) and the top 62 of the first toggle mechanism 61 is restrained by the stopper 97T, the rising motion energy of the cylinder device 82 (piston rod 85) becomes 74S is moved leftward by L1 shown in FIG. 6 (B). That is, the kinetic energy can be stored in the spring 92. Kinetic energy unrelated to the touch operation can be collected and held.

The magnitude of the stored energy corresponds to the vertical stroke locus of the piston rod 85 (top 72) in FIG.
(A) is represented as an area hatched. That is, as shown in FIG. 1, the lower roll 21 touches the lower surface of the plate material W, that is, the plate material W is
Accumulates only while is clamped at a predetermined pressing force.

Since the spring 92 contracts after the top 62 contacts the stopper 97T and restrains the position (roll touch), the spring 92 determines the magnitude of the force (pressing force) of the lower roll 21 pressing the plate material W. It also has important implications. In other words, by adjusting the strength of the spring 92, the pressing force can be adjusted.

On the other hand, when the piston rod 85 is in the downward direction (release operation direction) in FIG.
Releases the stored energy at once. That is, it works positively for the release operation. Therefore, a very high-speed release operation can be performed.

By the way, even if the cylinder device 82 is set to supply a large stroke and high-pressure air and the release operation is accelerated by the energy release by the energy storage means 91, the cylinder device 82 and the solenoid valve 87 are the same as the conventional example (FIG. 8). In a structure such as the electromagnetic switching valve 87P), for example, 200 to 30 per minute
It is considered that the speed is reduced to zero or more times.

Here, the release driving means 81 of this embodiment is used.
As shown in FIG. 1, the cylinder device 82 includes the aspirator 86 and a simple ON-OFF solenoid valve 87 to achieve a further higher speed. Although the solenoid valve 87 is shown in FIG. 1 as switching the positions A and B, it is only necessary to actually turn ON / OFF the exhaust port (pipe) 89E2 of the aspirator 86. Therefore, the solenoid 87S is excited,
Direct ON with movable core that rapidly displaces when de-energized
-Can be turned off. That is, the solenoid 87S is configured as shown in FIG.
For example, as shown in FIG.
I can do F. That is, the movable core is moved at a high speed and the exhaust pipe 8 is moved.
9E2 can be turned off.

Then, a chamber 86 containing a nozzle is provided.
A pipe 89S for guiding high-pressure air P1 (for example, 7.5 kg / cm ² g) from an air source (not shown) is connected to B, and a pipe 89E1 for connecting the nozzle outlet to one chamber 83T of the cylinder 83 is provided. It is connected. The other room 83
L is a predetermined pressure air P2 (for example, 5 kg / cm ² g)
Of air is supplied.

Therefore, if the solenoid 87S is turned off and the solenoid valve 87 is set to the position A (the exhaust pipe 89E2 is closed), the high-pressure air P1 passes through the aspirator 86 (chamber 86B) and is supplied to the one chamber 83T through the pipe 89E1. Therefore, the piston 84 can be moved up (touch operation) at a high speed. On the other hand, turn on the solenoid 87S
Then, at the position B (opening the exhaust pipe 89E2), a negative pressure is formed in the chamber 86B by the nozzle action,
The air in one chamber 83T is rapidly exhausted by the negative pressure. At this time, since the predetermined pressure air P2 is applied to the other chamber 83L, the exhaust operation and the air supply operation can be performed simultaneously and rapidly as a whole, so that the piston 84 can be moved down (release operation) at high speed.

More specifically, it works as shown in FIGS. First, when the solenoid 87S is turned on, the movable core starts moving, and the pipe 89E2 is opened. Then, the aspirator 86 creates a negative pressure by the high-pressure air P1, so that the rapid exhaust operation of the one chamber 83T of the cylinder 83 is started. At this time, the predetermined pressure air P2 is applied to the other chamber 83L. Therefore, the piston 84, that is, the piston rod 85, rapidly lowers the top 72 of the second toggle mechanism 71 downward in FIG.

That is, as shown in FIG. 5B, when the solenoid 87S is turned ON, for example, 0.012
After Sec, the energy stored in the spring 92 of the power storage means 91 is released at a stretch. Thus, the lower roll 21 can be quickly started to move in the separating (unclamping) direction from the lower surface of the plate material. Also, after 0.005 sec from the start of the unclap direction, 3/1000
Sec is completely unclamped.

On the other hand, when the solenoid 87S is turned off at the start of the unclamping direction, the movable core
Returning to the original state at 1000 sec, the position is switched to the position A in FIG. 1 and the pipe 89E2 is closed. Therefore, the high pressure air P
1 is one chamber 83T passing through the chamber 86B.
And the piston rod 85 starts to rise rapidly (clamp operation direction).

Thus, after 0.013 sec, the top 72 of the second toggle mechanism 71 is raised again in FIG. 1, and the first toggle mechanism 61 pushes up the lower roll 21 and starts to move in the clamping operation direction. Then, the top 62 becomes the stopper 97
Since the position is restricted by T, energy starts to be stored again in the storage means 91 (spring 92). The lower roll 21 is
With a predetermined and constant pressing force determined by the strength of the spring 92,
The plate material W is clamped.

The movement of the lower roll 21 during this time is as shown in FIGS. 6 (A) and 6 (B). Thus, the lower roll 21 clamps the plate material W within a predetermined crank angle as shown in FIG. 5C, during which the drive shaft 34 rotates to feed the plate material W, and the lower angle of the crank angle is 180 degrees. A release operation is performed for 3/1000 sec before and after including the point.

When the pressing speed is 1000 SPM, the time required for one rotation of the crankshaft is 3/5.
0Sec. Therefore, the crank angle allowed for the unclamping operation including the release operation is, for example, 150 degrees to 2 degrees.
Assuming that it is 30 degrees and 80 degrees, the time required for this 80 degrees is about 0.013 sec at 1000 SPM.
It is. However, in this embodiment, the unclamping operation including the release operation is performed as shown in FIGS. 5A and 5B.
It is executed at 0.013 sec. Therefore, it can be seen that the release operation can be easily performed 1000 times or more per minute.

Next, the operation of this embodiment will be described. FIG.
, When the rotation of the servo motor 32 forming the drive device 31 of the roll feeder 10 is started, the lower drive bevel gear 4
5 and the upper drive bevel gear 35 are simultaneously started to rotate. Here, the upper driving bevel gear 35 is urged by the upper urging means 37 and is properly meshed with the upper driven bevel gear 12, and the lower driving bevel gear 45 is also urged by the lower urging means 47 to be driven lower. It is properly meshed with the bevel gear 22.

Therefore, the bevel gear mechanism (12, 35)
Even if there is a mechanical backlash in each of the lower bevel gear mechanism and the lower bevel gear mechanism (22, 45), since the rotation is started simultaneously by the drive shaft, both rolls 11 and 21 are synchronized simultaneously and in opposite directions. Rotate. Therefore, since a feeding force can be applied to the plate material W clamped between the rolls 11 and 21 from both sides, the plate material W can be stably fed to the press with high accuracy.

When replacing the plate material W with a different thickness, the thickness-adjusting position adjusting device 50 is operated with the driving device 31 (servo motor 32) stopped. When the handle 51 is rotated, the screw shaft 55 (55) rotates and moves up (down) with respect to the machine frame 5. Therefore, the upper roll 11 (the axis H in FIG. 3) rotatably supported by the upper slider 15
h) can be moved up (down) within △ and easily adjusted to the thickness of the plate material W.

At this time, the upper driven bevel gear 12 integral with the upper roll 11 pushes the upper driving bevel gear 35 meshed with the upper driven bevel gear 35 upward. However, since the upper drive bevel gear 35 is mounted on the upper spline 34U of the drive shaft 34, it can move upward. In addition, even after the movement, it is urged in the direction of the upper driven bevel gear 12 by the upper urging means 37. Therefore, the meshing state of the upper bevel gear mechanism (12, 35) is
It can always be kept constant regardless of movement. Backlash is also constant.

Next, the release operation will be described. The timely generated signal S causes the solenoid 87S of FIG.
When it is turned on at the timing shown in (B), the movable core works, that is, the solenoid valve 87 is moved to the position B expressed simply.
Is switched. Then, the aspirator 86 generates a negative pressure, and the cylinder device 8 forming the release driving means 81
2 (in the cylinder 83), air is evacuated from one chamber 83T, and a predetermined pressure air P2 is applied into the other chamber 83L. Here, the cylinder device 82 includes a piston rod 85
The top 72 of the second toggle mechanism 71, which is connected to the first, is rapidly lowered downward in FIG.

Then, the top 62 of the second toggle mechanism 61 is
In FIG. 1, it is moved horizontally leftward and separates from the stopper 97T. At the same time, the stored energy is released at once from the spring 92 forming the storage means 91 to the top 72. Therefore, the piston cylinder 85 is pushed down more rapidly. Here, the lower roll 21 is unclamped by the first toggle mechanism 61 as shown in FIG. 5A, and the release operation is performed within a predetermined crank angle.

On the other hand, at the same time as the lower roll 21 starts the unclamping operation, the solenoid 87S is turned off as shown in FIG. 5B. Then, the solenoid valve 8
7 switches to position B. That is, since the pipe 89E2 is closed, the high-pressure air P1 is supplied into the one chamber 83T of the cylinder device 82 through the chamber 86B and the pipe 89E1.

Therefore, the piston rod 85 is
The top 72 of the toggle mechanism 71 is rapidly pushed upward in FIG. As a result, the top 63 of the first toggle mechanism 61 moves in the horizontal right direction, and the lower roll 21 is moved to the lower slider 25.
Begins to rise with. And the top 62 (head 98A)
Abuts on the stopper 97T and is restrained,
The lower roll 21 clamps the plate material W from the lower surface side.

Here, since the first toggle mechanism 61 acts as a whole as the fixed end, the other link 7 is operated by the subsequent ascent operation of the piston rod 85 (top 72).
4 moves the pin 74S to the left in FIG. That is,
The spring 92 is contracted by L1 shown in FIG. 6B, and its energy is accumulated as shown by hatching in FIG. 5A.

When the release driving means 81 (cylinder device 82) performs the release operation, that is, the top 72 descends and the top 62 moves horizontally leftward in FIG. When it is separated from the lower surface, it is released at a stretch via the other link 74.

Thus, the first toggle mechanism 61 and the second toggle mechanism 71 of the release device 60 operate as shown in FIG. 6B, and as a result, the lower roll 21 is moved as shown in FIG. 6A and FIG. Thus, the clamp-roll touch-unclamp operation is performed. In this case, the release amount is as small as Hc (0.5 mm) shown in FIG. 6 and the release driving means 81 (82, 86, 87) operates at a high speed as shown in FIG. Operation can be easily achieved.

By the way, during the release operation, when the lower roll 21 shown in FIG. 3 moves up and down together with the lower slider 25 (down from the height Hl by Hc in FIG. 6), the lower driven bevel gear 22 moves the lower drive bevel gear 45. Press down on shoe 46
Is connected to the drive shaft 34 via the bracket 48, so that the lower drive bevel gear 45 is pushed down together with the drive shaft 34. The drive shaft 34 (spline 34D) moves relative to the spline member 33. Therefore, the meshing of the lower bevel gear mechanism (22, 45) does not come off. Backlash is also constant. This is the same even when the lower roll 21 moves up.

On the other hand, even when the drive shaft 34 moves up and down in this way, the upper drive bevel gear 35 is mounted on the drive shaft 34 via the upper spline 34U, so that the upper bevel gear mechanism (12,
The engagement of 35) is not disengaged and has no effect. Therefore, while the drive shaft 34 is rotating, the two rolls 11 and 21 can always be rotated synchronously even if the release operation is performed. The drive shaft 34 is rotated by the servomotor 32, and feeds the plate material W (FEE).
D) is performed only at 180 degrees of 270 to 90 degrees shown in FIG.

According to this embodiment, the urging means 95 is attached to the first toggle mechanism 61 for moving the roll (21) of the double toggle mechanism (61, 71) up and down, and is driven by the release driving means 81. The storage means 91 is attached to the second toggle mechanism 71 to be operated, and a stopper 97T for restraining the horizontal position of the top 62 of the first toggle mechanism 61 is provided before the cylinder device 82 becomes a full stroke in the touch operation direction, The second toggle mechanism 7 at the start of the release operation
Since the configuration is such that the stored energy is released to the top 72 as the urging force in the release operation direction, the release operation can be performed at a high speed, and the timing can be easily set, and the plate material can be supplied with stability and high accuracy.

Further, since the release device 60 is formed including the double toggle mechanism (61, 71), the roll touch operation can be lengthened and the unclamping / clamping operation can be performed in a timely manner, so that the drive timing can be easily set. it can.

Further, since the first toggle mechanism 61 of the release device 60 is connected to the urging means 95 for holding the weight of the lower roll 21, the lower slider 25, etc., the release drive means 81 (cylinder device 82). , And the driving speed can be reduced.

Since the top 62 of the first toggle mechanism 61 is restrained in the horizontal position by the stopper 97T, the pressing force of the plate material W can be kept constant. Further, the stroke operation of the cylinder device 82 may be rough. By adjusting the spring 92, the pressing force can be adjusted.

Further, since the energy storage means 91 is connected to the second toggle mechanism 71, the release operation of the stored energy can greatly speed up the release operation.

Further, since the release driving means 81 is formed by the cylinder device 82, the aspirator 86 and the solenoid valve 87, the release driving means 81 can be driven at a high speed, and the release amount can be minimized and the stored energy can be released. For example, one per minute
Release operation can be performed at a remarkably high speed of 000 times or more.

Further, since the release operation direction of the lower roll 21 and the operation direction of the cylinder device 82 are parallel (Z1, Z2), a smooth operation can be guaranteed.

Further, the upper driven bevel gear 12 is
And the lower driven bevel gear 22 is mounted on the lower roll 21, and the upper driving bevel gear 35 and the lower driving bevel gear 45 are fitted on the driving shaft 34 via splines 34U and 34L. Is provided with an upper urging means 37 for properly meshing the lower driven bevel gear 12 with the upper driven bevel gear 12, and a lower urging means 47 for properly meshing the lower driving bevel gear 45 with the lower driven bevel gear 22. Can be established a double roll drive system that eliminates the problem. Therefore, upper and lower roll 1
1 and 21 can be rotated completely synchronously, and a high-precision plate material feed can be performed. At the same time, the release amount can be further reduced, and the high-speed release operation can be further performed.

Further, the upper roll 11 and the lower roll 21
Are attached to the machine frame 5 via the upper slider 15 and the lower slider 25 so as to be independently liftable,
And a position adjusting device 50 corresponding to the thickness of the upper roll 11 (15).
Are connected, so that the release amount can be a minimum value (for example, 0.5 mm) required for the purpose.
The release operation can be performed at a higher speed.

[0085]

According to the present invention, the biasing means is attached to the first toggle mechanism for vertically moving the roll of the double toggle mechanism, and the energy storage means is attached to the second toggle mechanism driven by the release driving means. A stopper is provided for restraining the horizontal position of the top of the first toggle mechanism before the cylinder device reaches the full stroke in the touch operation direction, and the energy stored as an urging force in the release operation direction is applied to the top of the second toggle mechanism at the start of the release operation. Because it is a configuration that emits
The release operation can be performed at a remarkably high speed, for example, 1000 times or more per minute, and the timing can be easily set, and the plate material can be supplied with stability and high accuracy.

[Brief description of the drawings]

FIG. 1 is a side sectional view showing an embodiment of the present invention.

FIG. 2 is a plan view of the release device with a partial cross section.

FIG. 3 is a front sectional view of the same.

FIG. 4 is a plan view of the lower roll as viewed from above.

FIG. 5 is a view for explaining the operation of the release device including the energy storage means.

FIG. 6 is a view for explaining the operation of the double toggle mechanism.

FIG. 7 is a view for explaining an example in which a thickness-adjustable position adjusting device and a release device of a conventional example are also used.

FIG. 8 is a view for explaining another example in which the thickness-adjustable position adjusting device and the release device of the conventional example are also used.

FIG. 9 is a view for explaining the operation of a conventional release driving means.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Press 2 Pilot pin 5 Machine frame 10 Roll feeder 11 Upper roll 12 Upper driven bevel gear 15 Upper slider 16 Spring 21 Lower roll 22 Lower driven bevel gear 25 Lower slider 26 Spring 31 Drive device 32 Servo motor 33 Spline member 34 Drive shaft 34U Upper spline 34L Lower spline 34D Spline 35 Upper drive bevel gear 36 Shoe 37 Spring 45 Lower drive bevel gear 46 Shoe 47 Spring 48 Bracket 50 Thickness corresponding position adjusting device 51 Handle 52 Shaft 55 Screw shaft 56 Nut member 60 Release device 61 First Toggle mechanism 62 Joint (top) 63 One link 63S pin 64 Other link 64S pin 71 Second toggle mechanism 72 Joint (top) 73 One link 74 Other link 74S pin 81 Release driving means 82 Sunda apparatus 83 cylinder 83T one chamber 83L other chamber 84 piston 85 piston rod 86 the aspirator 87 solenoid valve 87S solenoid 91 accumulating means 92 the spring 93 connecting member 94 guide member 95 biasing means 96 spring 97 cylinder body 97T stopper 98 connecting member

Claims (1)

(57) [Claims] 1. A roll feeder (10) for rotating one of an upper roll (11) and a lower roll (21) for supplying a sheet material in a predetermined direction while rotating and holding the plate in a timely manner by a predetermined release amount. A first toggle mechanism (61) for causing one of the upper roll and the lower roll to perform a release operation and a touch operation along a vertical axis (Z1) facing the other roll; and a cylinder device. Top (72) moved up and down by (82)
And a second toggle mechanism (71) for horizontally reciprocating the top (62) of the first toggle mechanism via one link (73), and a pair of links (63, 63) forming the first toggle mechanism. 64)
To the top (6) so as to be linear along the vertical axis.
Urging means (95) for applying a constant urging force to 2), and a top (6) for forming a first toggle mechanism before the full stroke in the touch operation direction of the cylinder device (82) is reached.
2) Stopper for restraining horizontal position (97T)
The other end of the link (74) forming the second toggle mechanism is connected to the fixed end side, and the top (62) of the first toggle mechanism is restrained in position by the stopper. A power storage means (91) formed so as to store kinetic energy and release the energy as a biasing force in the release operation direction to the top (72) of the second toggle mechanism at the start of the release operation. Release equipment.