JP2522138Y2 - Hydraulic scrap cutter for press machine - Google Patents

Description

[Detailed description of the invention]

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic scrap cutter for a press machine. In particular, it has both a high-speed and low-shear capacity function during a scrap-cut operation and a low-speed and high-shear capacity function during a coil full-cut operation.

[0002]

2. Description of the Related Art On the downstream side of a press machine, a scrap feeder and a scrap cutter device for discharging a coil after press working are arranged. This scrap cutter device includes a mechanical drive type, an electric drive type, and a hydraulic drive type.

[0006] A mechanically driven scrap cutter apparatus 10 P shown in FIG. 6 uses an upper blade 11 attached to an upper blade holder 16 and a lower arm member for a lower blade 21 attached to a lower blade holder 26 on the bed 3 side. 19, it is configured to move up and down synchronously with the slide 2 of the press machine 1. In addition,
The upper blade holder 16 is biased by a spring to balance the weight. Therefore, the upper blade 11 can be moved up and down in synchronization with the operation of the press machine 1. That is, while the coil C sent in the direction of the solid arrow shown in FIG. 7 is stopped, the scrap cut line SC
Can be sheared on. However, this mechanical drive type has a problem that an eccentric load is applied to the press machine 1 so that the life of the die is shortened.

On the other hand, the electric drive type is a press machine 1
And a separate system, and is formed by an electric motor and a power transmission mechanism. Therefore, the eccentric load is not transmitted to the press machine 1, but the size of the apparatus becomes large, so that the cost increases and the layout is hindered. In this regard, the hydraulic drive type that employs a cylinder device that directly raises and lowers the upper blade 11 is compact and low-cost.

By the way, such a scrap cutter device 1
0P is used not only for the scrap cut line SC shown in FIG. 7 but also for the case where the coil C is sheared by the coil full cut line FC. When the pressing is completed, the coil C is rewound in the direction of the uncoiler (in the direction of the dotted arrow). As a condition for smoothly performing the next sheet passing, the coil is to have a flat end shape without a notch (EH) at the tip of the coil.

[0006]

Thus, even with a compact and low-cost hydraulic drive type that does not generate an eccentric load, the pressure generating capability, that is, the shearing capability, can be reliably operated even at the maximum value when the coil is fully cut. The capacity has been selected. Therefore, according to such a conventional structure, the present device 1
It can be said that the capacity is too large for the original purpose of scrap cutting of 0P.

[0007] Further, because of the excessive capacity, the amount of hydraulic pressure supplied to and discharged from the cylinder device becomes large. The amount of the oil hardly changes because the upper blade 11 needs to be moved up and down by the same amount at the time of the coil full cut requiring high shearing force or at the time of scrap cutting which may be low shearing force. Thus, even when the shearing force is low, the same time as when the shearing force is applied to the upper blade 11 needs to be lifted and lowered. Therefore, if a further increase in the press speed is required, the press working is stopped after the coil feeding is stopped. Until the time (e.g., a crank angle of 120 to 180 degrees), and then the upper blade 11 as soon as possible.
Is difficult to lift to the limit. That is, the high-speed operation of the press machine 1 cannot be followed. There is also a problem that waste energy due to an excessive amount of oil is consumed during scrap cutting.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a hydraulic scrap cutter device for a press machine having both a high-speed / low-shear capacity function and a low-speed / high-shear capacity function. .

[0009]

SUMMARY OF THE INVENTION The present invention has a basic structure of a hydraulic drive type which can eliminate the generation of eccentric load of a mechanical drive type and an increase in size and cost of a separately-driven electric drive type. Focusing on the fact that there is a significant difference in the required shearing force from the full-cut operation that is difficult to avoid, it is configured to ensure high-speed followability to the press machine by reducing the shearing ability during the scrap-cut operation.

That is, the hydraulic scrap cutter device for a press machine according to the present invention includes a first cylinder device connected to an upper blade, a second cylinder device weighted to the first cylinder device, and an interlocking device with the press machine. And a drive control means for controlling the drive of the first cylinder device during the scrap-cut operation and simultaneously controlling the drive of the first and second cylinder devices during the coil full-cut operation.

[0011]

In the present invention having the above configuration, in the case of the scrap cutting operation, the drive control means controls the drive of the first cylinder device. Although the shearing ability is low, the amount of oil supply / discharge is small, so that it can be driven quickly. Therefore, the scrap can be cut smoothly and the press machine can follow the press machine at a high speed, and the energy consumption can be reduced. On the other hand, in the case of the coil full cut operation, the drive control means controls the drive of the first cylinder device and the second cylinder device simultaneously. Therefore, since the operation can be performed with a large shearing power determined as the sum of the pressure generated by the first cylinder device and the pressure generated by the second cylinder device, a wide coil without a notch after pressing can be smoothly full-cut. In the case of the coil full-cut operation, the operation is slowed down because the amount of oil supplied to both cylinder devices is increased, but there is no problem because it is not necessary to follow the press machine.

[0012]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below with reference to the drawings. As shown in FIGS. 1 to 4, the scraper cutter (10) includes an upper blade 11, a lower blade 21, a pressure generator 31 (first cylinder device 32, second cylinder device 42), and first hydraulic systems 51, 51. , A second hydraulic system 61, and a drive control means (drive control panel 70), and has both a high-speed / low-shear capacity function and a low-speed / high-shear capacity function.

In FIG. 1, slide 2, bolster 4
On the downstream side in the flow direction X of the coil C of the press machine 1 including the (bed 3) and the like, the scrap feeder 5 and the device 10
And are arranged in a row. Since the device 10 is of a hydraulic drive type, it is compact as shown. 6 is a shoot. Also in the case of the present embodiment, the same coil C as in the conventional example (FIG. 7) is used, and shearing is performed at the scrap cutting line SC during the scrap cutting operation, and at the coil full cutting line FC during the coil full cutting operation.

As shown in FIG. 2, the upper blade 11 is held (fixed by bolts 37) on an upper blade holder 16 slidably mounted on a guide post 13 in a vertical direction. The bolt 14 implanted in the cylinder block 12 is urged by a spring 15 mounted on the cylinder block 12 to balance the weight. The lower blade 21 is connected to the machine frame 2 via a lower blade holder 26.
2 is fixedly arranged. The upper limit of the upper blade 11 is detected by an upper blade upper limit sensor 72, and the lower limit of the upper blade 11 is detected by an upper blade lower limit sensor 73. 72d and 73d are dogs fixed to the upper blade holder 16 so as to correspond to the respective dogs.

As shown in FIG. 2, the pressure generating device 31 includes a lower first cylinder device 32 (a cylinder 33, a piston 34, an upper chamber 35U, and a lower chamber 35D) and a weighted upper upper cylinder device 32. The second cylinder device 42 (cylinder 43, piston 44, upper chamber 45U, lower chamber 45D) is integrally mounted. Each cylinder 33, 43 is formed as a part of the cylinder block 12. 46 is a cylinder head.

That is, the pressure generating surface of the first cylinder device 32 is small and has a small area A1 shown in FIG.
The cylinder device 42 is of a large size having a large area A2, and the piston 44 is provided with an upper chamber 35U of the first cylinder device 32.
It can protrude into. When the first cylinder device 32 and the second cylinder device 42 are driven at the same time, the first cylinder device 32 has a large shearing capacity required at the time of full cutting, and if only the first cylinder device 32 is driven, it switches to the small shearing capability required at the time of scrap cutting. Can drive. In this embodiment, A1 =
A2 × １ ／. That is, the first cylinder device 3
2 is set to 25% or less of the required maximum generated pressure at the time of full cut. Depending on the form and arrangement density of the perforated portion EH of the coil C, it can be set to 20% or less.

Next, as shown in FIG. 3, the first hydraulic system of the first cylinder device 32 has two systems (51, 51). One series of second hydraulic system 6 of second cylinder device 42
1 is provided separately. The reason why the first hydraulic system of the first cylinder device 32 has two systems (51, 51) is to further enhance the high-speed followability while coping with the reduction in the amount of oil supply / discharge. When the first hydraulic system 51 (51) switches from the position E to the position U by exciting (ON) the hydraulic switching valve 54 to which the supply pipe 58 and the discharge pipe 59 are connected and the solenoid SV11 (21). A rising oil pipe 52 for supplying hydraulic pressure to the lower chamber 35D of the first cylinder device 32;
When the solenoid SV12 (22) is energized (ON) and switched to the position D, it comprises a descending oil pipe 53 that supplies oil pressure to the upper chamber 35U. On the other hand, the second hydraulic system 61 includes a hydraulic pressure switching valve 64, an ascending oil pipe 62, and a descending oil pipe 63, and the solenoids SV31 and SV32 and the respective positions U, E,
The operation relationship with D is the same as that of the hydraulic switching valve 54. In addition, 57 is an accumulator.

The drive control means includes a drive control panel 7 shown in FIG.
0. In the case of this embodiment, the drive control panel 70 is formed of a microcomputer including a CPU, a ROM, and a RAM. The input port is provided with a coil in addition to the above-described upper blade upper limit sensor 72 and upper blade lower limit sensor 73. Coil feeder 5 for detecting feed amount of feeder 5
The rotary cam switch 77 for taking the interlock timing between the counter 75 in the inside and the press machine 1 is connected,
The output ports are connected to the respective solenoids SV of the respective hydraulic pressure switching valves 54, 54, 64 as shown in the figure. The counter 75 is formed by a CPU, and 71 is a switch for switching between a continuous scrap cutting operation and a coil full cut operation performed prior to the coil rewind operation.

In this case, the drive control means (70) performs both first and second cutting operations during the scrap cutting operation linked with the press machine 1.
The two first cylinder devices 32,
32 (ST12 to ST16 in FIG. 5), and the first hydraulic system 51, 5 during the coil full cut operation.
First and second cylinder devices 3 using the first and second hydraulic systems 61
2, 32 and both second cylinder devices 42, 42 are simultaneously driven (ST20 to ST23).

Next, the operation of this embodiment will be described. After the coil C is passed through the press machine 1 and passed through the scrap feed 5, the press operation starts. Prior to this, the changeover switch 71 shown in FIG. 4 is switched to the continuous operation. At this time, the solenoids SV11, SV21, SV31 shown in FIG.
N), and the upper blade 11 is at the upper limit (ST10 in FIG. 5, YES in ST11).

During the press operation, the coil C is fed by one stroke in the arrow X direction shown in FIG. 1 when the crank angle θi is, for example, 240 to 0 to 120 degrees. Here, while the crank angle θi is, for example, 120 to 180 degrees and the coil C is stopped (YES in ST12, YES in ST13)
Then, the drive control means (70) switches the hydraulic switching valves 54, 54 of the first hydraulic system 51, 51 to the positions D, D.
Performed by turning on the solenoids SV12 and SV22 (ST
14). Therefore, by lowering the pistons 34, 34 of the first cylinder devices 32, 32 and lowering the upper blade 11 at high speed from the upper limit shown by the solid line in FIG. 1 to the lower limit shown by the two-dot chain line, the lower blade 21 In cooperation, the coil C can be cut along the scrap cut line SC shown in FIG. Scrap cutting can be performed smoothly even with a low shearing capacity.

The upper blade 11 is detected by the upper blade lowering limit sensor 73.
Is detected to have reached the lower limit (YES in ST15).
And the drive control means (70)
V22 is turned off and the solenoid SV11,1
2 is turned ON (ST16). That is, since each of the hydraulic pressure switching valves 54, 54 is switched to the position U, U, the pistons 34, 34 connected to the upper blade holder 16 are raised to raise the upper blade 11 to the upper limit. This state is confirmed by the upper blade rising end sensor 72 (ST1).
1). Hereinafter, the scrap cutting operation is performed in conjunction with the press machine 1 by repeating this operation.

On the other hand, when the coil C is wound around the uncoiler after the press is stopped, the changeover switch 71 is switched to the coil full cut operation (NO in ST12). Then, the drive control means (70) feeds the coil C by the preset feed amount by the coil feeder 5 and detects this by the counter 75 in the coil feeder 5, that is, the entire width of the coil C is changed to that shown in FIG. (S20: YES), the solenoids SV12, SV22, and SV32 are simultaneously turned on (S20).
T21). Then, both first cylinder devices 32, 32 and both second cylinder devices 42, 42 operate simultaneously. That is,
The upper blade 11 is lowered to generate a large pressure, and the coil C is fully cut. When the upper blade 11 reaches the lower limit (YES in ST22), the solenoids SV11, SV21, S
The upper blade 11 is raised by turning on V31. Therefore, if the coil C is rewound in the direction of the dotted arrow in FIG. 7 after the completion of the full cut, the leading end of the coil C has a flat end shape that does not touch the perforated portion EH, so that the next passing plate can be smoothly performed. That is, the conditions for automating coil passing can be satisfied.

Thus, according to this embodiment, the first cylinder device 32 and the second cylinder device 42
And a separate hydraulic system 51, 61 is provided for each of the cylinder devices 32, 42, and the drive control means (7
0), the upper blade 11 is moved up and down by the lower first cylinder devices 32, 32 during the scrap cutting operation, and the two cylinder devices 32, 42, 32, 4 during the coil full cutting operation.
2 are simultaneously driven to move the upper blade 11 up and down, so that high-speed and low-shearing capacity can be achieved during scrap cutting operation, and low-speed and high-shearing ability can be achieved during coil full-cut operation. Can be performed. Therefore,
It is possible to establish a compact, low energy consumption hydraulic scrap cutter device capable of high-speed follow-up operation to the press machine 1 while solving the problem of the generation of eccentric load by the conventional mechanical drive type and the problem of increasing the size of the separately mounted electric drive type.

The first cylinder devices 32, 32
Since there are two hydraulic systems (51, 51), the raising and lowering operation of the upper blade 11 during the scrap cutting operation can be performed at a higher speed. On the other hand, the second used during low-speed full-cut operation
Since the structure is simplified by using one hydraulic system (61), the cost is reduced.

Further, since the pressure generation area A1 of the first cylinder device 32 and the pressure generation area A2 of the second cylinder device 42 are set to A1 = A2 × １ ／, energy consumption during continuous operation can be greatly reduced. .

[0027]

According to the present invention, the first blade connected to the upper blade is provided.
A cylinder device, a second cylinder device weighted to the first cylinder device, and a drive control means are provided, and during a scrap cutting operation linked to a press machine, the first cylinder device is drive-controlled to raise and lower the upper blade. During the full cut operation, the first and second cylinder devices are simultaneously controlled to drive the upper blade up and down, so that the scrap cut operation has a high speed and low shearing ability, and the full cut operation has a low speed and a high shear capacity. Smooth cutting work can be performed for each with shearing ability. Therefore, it is possible to solve the problem of the eccentric load caused by the conventional mechanical drive type and the problem of increasing the size of the separately mounted electric drive type, and it is possible to operate the press machine at a high speed following a compact press machine with excellent energy saving and small energy consumption. Can be provided.

[Brief description of the drawings]

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

FIG. 2 is a front view in which one side is similarly sectioned.

FIG. 3 is a diagram for explaining the relationship between each cylinder device and each hydraulic system.

FIG. 4 is a block diagram for explaining a drive control unit.

FIG. 5 is a flowchart for explaining the operation.

FIG. 6 is a side view for explaining a conventional example (mechanical drive type).

FIG. 7 is a diagram for explaining a relationship between a coil and a cut line.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Press machine 2 Slide 3 Bolster 4 Bed 5 Scrap feeder 6 Chute 10 Scrap cutter device 11 Upper blade 12 Cylinder block 13 Guide post 14 Bolt 15 Spring 16 Upper blade holder 19 Arm member 21 Lower blade 22 Machine frame 26 Lower blade holder 31 Pressure Generator 32 First cylinder device 33 Lower cylinder 34 Lower piston 35U Upper chamber 35D Lower chamber 42 Second cylinder device 43 Upper cylinder 44 Upper piston 45U Upper chamber 45D Lower chamber 46 Cylinder head 51 First hydraulic system 52 Up oil pipe 53 Down oil pipe 54 hydraulic switching valve 57 accumulator 58 supply pipe 59 discharge pipe 61 second hydraulic system 62 rising oil pipe 63 descending oil pipe 70 drive control panel (drive control means) 71 changeover switch 72 upper blade rise limit sensor 72d dog 3 upper blade descent limit sensor 73d dog 75 in the coil feeder counter 77 Rotary cam switch

Claims (1)

(57) [Scope of request for utility model registration] 1. A first cylinder device (32) connected to an upper blade (11), a second cylinder device (42) weighted to the first cylinder device, and a press machine (1) interlocked. A drive control means (70) for controlling the drive of the first cylinder device during the scrap cut operation and for simultaneously controlling the drive of the first and second cylinder devices during the coil full cut operation. Hydraulic scrap cutter device.