JPS6238723A - Bending machine - Google Patents

Abstract

PURPOSE:To improve the bending accuracy of a product by calculating a pressure supporting force corresponding to a work condition of a plate bending work, and also generating an optimum pressure force to a work piece, based on its pressure supporting force. CONSTITUTION:The titled machine is provided with plural pressure cylinders 43F, 43R for pressing a work piece W between top dies 41F, 41R and bottom dies 21F, 21R. Bend beams 47F, 47R are attached to the upper part of bending rams 49F, 49R in order to bend the end edge of the work piece W, and move up and down through bending cylinders 61F, 61R. An optimum pressure supporting force between a bottom die 21 and a top die 41 corresponding to a plate thickness, a material quality, and a bending width of the work piece W is calculated in advance in a pressure force operation module. Subsequently, a bend beam 47 executes bending by this pressure supporting force. Accordingly, a deflection of a fixed frame is prevented, and the bending accuracy can be improved.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a machine that bends a plate-shaped workpiece, and more specifically, the present invention relates to a machine that bends a plate-shaped workpiece. This invention relates to a machine that holds the workpiece horizontally and bends the edge of the workpiece into, for example, a box shape.

[Description of Prior Art] A tangent bender, for example, is known as a machine that bends the edge of a plate-like workpiece into an L-shape. A tangent bender consists of a bottom die that supports the workpiece from below, a vertically movable top die that presses the bottom die, and a top die that presses the workpiece from above against the bottom die. It is equipped with a rotatable bend beam that bends the edge of the workpiece upward.

However, with this type of bending machine, it may be difficult to optimize the pressing support force between the bottom die and the top die to improve product accuracy. 5, -A5, yo, 5i, tsua ゛□K a
onci □8, ka, 9 ergo, a, 1 ・)-
When the beam is applied, the workpiece is pulled toward the bend beam by the bending pressure of the bend beam. This drawn-in suspension becomes smaller as the ratio of the pressing support force P to the bending pressure B (A=P/B) increases, and once this ratio A reaches a certain value, it becomes almost constant after that. It is known. Therefore, as far as this goes, it seems that the larger the ratio A of the pressing support force to the bending pressure is, the better.

On the other hand, in general, in a bending machine, the above-mentioned pressing support force P is generated by applying it between a fixed frame and a bottom die or between a fixed frame and a top die. and,
These fixed frames have a predetermined stiffness value. Therefore, if the ratio A is increased beyond a certain level, the fixed frame will be warped, and the workpiece will also be warped.

For this reason, there is a value for the ratio A of the pressing support force F to the bending pressure P that does not increase the warpage of the fixed frame and at the same time keeps the retraction (a) below a predetermined amount. With conventional bending machines, this value cannot be optimized and the amount of retraction is made too large, resulting in poor product accuracy or warping of the product.

[Object of the invention] The object of the present invention is to provide a bending machine that can improve the above-mentioned problems, optimize the pressing support force of the workpiece between the bottom die and the top die, and improve the product accuracy. shall be.

[Summary of the Invention 1 In order to achieve the above object, the present invention provides a bottom die and a top tie that protrude a workpiece of a predetermined width by a predetermined amount and support it with a predetermined pressing force, and a bottom die and a top tie that protrude from the bottom die and the top tie. a bend beam that bends a protruding portion of the workpiece by moving in a direction perpendicular to the workpiece; a calculation means that calculates the pressing support force according to the type of bending work; A bending machine includes a pressure support force providing means for applying the pressure support force calculated by the calculation means to the hem die and the top die of the bod 1, and the bending machine comprises a pressure support force providing means for applying the pressure support force calculated by the calculation means to the bottom die and the top die according to the type of work of the bending process. The pressure support force applied to the top die has been optimized.

[Description of Example 1 An embodiment of this invention will be described below.

FIG. 1 is a front view of a bending machine embodying the present invention;
Figure 2 is a side sectional view taken along the line ff-I in Figure 1, Figure 3 is an enlarged view of the part marked by the arrow ■ in Figure 2,
The figure is an explanatory side cross-sectional view taken along the line IV-■ in FIG. 3.

Referring to FIGS. 1 and 2, a bending machine for bending the edge of a plate-shaped workpiece W is generally designated by the reference numeral 1. The frame body 3 constituting the bending device 1 includes a base 5, left and right side frames 7.9 vertically erected from both ends of the base 5, and both left and right ends supported by the upper part of the side frames 7.9. The upper beam member 11F, 11'R, etc. are separated from each other in the front and rear.

Support plates 13A and 13B extending in the front-rear direction and left-right direction are erected near the center in the left-right direction and near the center in the front-rear direction of the base 5, and one support plate extends in the left-right direction. Both ends of 13B are connected to the side frame 7.9. A horizontal plate 15 whose left and right ends are connected to the side frame 7.9 is supported on the upper part of these support plates 13A and 13B. A plurality of connected die support plates 17F and 17R are erected and spaced appropriately in the front-rear direction. The front and rear die supports 17F and 17R are connected to each other by a plurality of connecting members 19 extending in the front-rear direction, and the front and rear die supports 17F and 17R are connected to each other by a plurality of connecting members 19 extending in the front-rear direction. 21F and 21R are supported respectively.

The bottom dies 21F and 21R support the workpiece W from below, and the bottom dies 21F and 21R support the workpiece W from below.
In order to detect the width dimension of the workpiece W, appropriate sensors 23F, such as limit switches or proximity switches, are installed on appropriate front and rear surfaces of each of 2'lR.
A plurality of 23Rs are arranged at appropriate intervals. Each sensor 2 above
3F and 23R are arranged corresponding to a plurality of rotary actuators 25F and 25R, which will be described later. Each sensor 23F and 23R detects the presence or absence of a workpiece W, and thereby controls the rotary actuator in accordance with the width of the workpiece. It functions to control the operation of actuators 25F and 25R.

Furthermore, as can be understood from FIGS. 1 and 2, a ram 27 is disposed above the bottom dies 21F and 21R so as to be movable up and down. The ram 27 has a longitudinal width larger than the distance between the front and rear bottom dies 21F and 21R, and extends significantly in the left-right direction. The left and right sides of the ram 27 are
It is pivotally connected to the piston rod 31R of the left and right lifting cylinders 31 mounted on the inner surface of the side frame 7.9 via a bracket 29. Therefore, the ram 27 is moved up and down by the operation of the lifting cylinder 31.

In order to vertically guide the ram 27, a guide block 33 is installed vertically at the center of the rear surface of the upper beam member 11F, and a trapezoidal guide bracket 35 is erected at the center of the upper surface of the ram 27. It is. A plurality of three roller brackets each having a rotatable guide roller 37 that can be moved around the vertical side surface of the guide block 33 are attached to the guide bracket 35. Therefore, the ram 27 is guided by the guide block 33 and vertically moves up and down as the lifting cylinder 31 operates.

The bottom die 21 is located at the front and rear of the lower surface of the ram 27.
Top dies 41F and 41R for pressing and fixing the workpiece W are removably attached to F and 21R, respectively. The top dies 41F and 41R are used by combining a plurality of divided pieces with appropriate dimensions into an appropriate length according to the width of the workpiece W.

A plurality of pressing cylinders 43F, 43R for pressing and supporting the workpiece W between the top dies 41F, 41R9 and the bottom dies 21F, 21R are mounted at appropriate intervals on the lower surfaces of the upper beam members 11F, 11R. Further, on the upper surface of the ram 27, each pressing cylinder 43F, 43
The plurality of rotary actuators 25F described above correspond to R.

25R is installed, and each rotary actuator 2
The rotating wheels of 5F and 25R include the pressing cylinder 43F,
Position directly below 43R and pressing cylinders 43F, 43R
1-shaped movable blocks 45F and 45R that can be moved freely from directly below to a remote position are attached.

The movable blocks 45F and 45R are operated in accordance with the operation of each sensor 23F and 23R that detects the workpiece W. Therefore, only the movable blocks 45F, 45R at the position corresponding to the workpiece W are positioned directly below the respective pressing cylinders 43F, 43R, and only the portion of the ram 27 corresponding to the workpiece W is positioned directly below the pressing cylinders 43F, 43R. 43R makes a loud noise. As a result, even if the workpiece W is unevenly distributed on either side of the left or right side, the workpiece W
This allows the pressure to be applied evenly.

The bottom die 21 is formed by the top dies 41F and 41R.
Bend beams 47F and 47R are provided inside the bottom dies 21F and 21R so as to be movable up and down in order to upwardly bend the edge portions of the workpiece W press-fixed to the bottom dies 21F and 21R. More specifically, bend beam 47F,
47R is a bending ram 49F, 4 which is provided to be able to move vertically.
9R, and the lower part of each bending ram 49F, 4'9R is attached to the eccentric shaft 53F, 53R, which is rotatably supported on the horizontal plate 15 via a plurality of brackets 51F, 51R. It is fitted and supported in the section. Therefore, the eccentric shafts 53F, 53
Rotate R appropriately to raise each bending ram 49F, 49R, and move each bend beam 47F, 47R to the bottom die 2.
By raising the 1F and 21R above the upper surface, the top dies 41F and 41R cause the bottom dies 21F and 2
The edge of the workpiece W supported by 1R can be bent upward.

The bending rams 49F, 49R are biased inward by 1q by appropriate springs 55F, 55R such as coil springs mounted between the die support plates 17F, 17R. And each bending ram 49F,
The large inclination of each bending ram 49F, 49R is restricted by the restriction portions tJ57F, 57R provided on the connecting member 19, which is inserted through the notch 7I9N of 49R.

In order to rotate the respective centers 53F and 53R, each eccentric shaft 53F and 53R is provided with an arm member 59F, respectively.
59R is integrally attached, and each arm member 59F,
The tips of the pistons 3F and 63R of the bending cylinders 61F and 61R are pivotally connected to the tip of the bending cylinder 59R via a pin.

Therefore, the screw 1 of each bending cylinder 61F, 61R
By expanding and contracting the hen rods 63F and 63R, the eccentric shafts 53F and 53R are rotated.

The bases of the bending cylinders 61F and 61R are pivotally connected to brackets 65F and 65R fixed to the base 5.The bending cylinders 61F and 61R control the strokes of the piston rods 63F and 63R. It is structured so that it can be changed at any time.

That is, the details will be omitted (although the strokes of the piston rods 63F, 63R in the bending cylinders 61F, 61R can be arbitrarily adjusted by controlling the motor M1, and the eccentric shaft 53F).

The amount of rotation of 53R can be adjusted.

When bending the edge portion of the workpiece W by the bend beams 47F, 47R, the bend beams 47F, 47
Wedge-shaped guide portions 067F and 67R for directing R toward the top dies 41F and 111R are mounted on the lower surface of the ram 27 so as to be vertically adjustable. More specifically, a plurality of kite portions 69 are vertically disposed in the central portion of the ram 27 in the front-back direction and are spaced apart from each other at appropriate intervals in the left-right direction, and the wedge-shaped guide members 67F, 67R
are firmly connected to each other, and each wedge-shaped guide member 67F.

An inclined surface 67R is formed so as to guide the upper sides of the bend beams 47F and 47[1] to the tube dies 41F and 41R. Therefore, the bending cylinder 6
Bend beams 47F and 47 are activated by 1F and 61R.
When R is raised to bend the end of the workpiece W, the bend beams 47F, 47R are guided by the wedge-shaped guide member 67.
F and 67R are directed toward the top dies 41F and 41R, and the edge portions of the workpiece W are bent.

The bending machine 1 according to this embodiment is shown in FIG.
One bottom die 21F and top die 41 from the left
After positioning the workpiece W to be transferred between the workpiece F and the workpiece W, one end edge (the end edge in FIG. 2) of the workpiece W is bent. Thereafter, the ram 27 is raised by the lifting cylinder 31 to release the pressure support of the workpiece W, and the workpiece W is transferred to the right in FIG.
After the workpiece W is pressed and supported by the other bottom die 21R and top die 41R, the other edge (the left edge in FIG. 2) of the workpiece W is bent.

A positioning device 71 is provided for positioning both end edges of the workpiece W when bending the both end edges of the workpiece W as described above. Although detailed illustration is omitted, a plurality of the positioning devices 71 are arranged at appropriate intervals between the bend beams 47F and 47R. In order to position the edge of the workpiece W, the collars 1 to 73, which are operated by the positioning device 71, are provided so as to be freely positionable in the left and right direction in FIG. It is provided so as to be freely recessed into the pass line of the workpiece W so as not to interfere with the workpiece W at times.

Depending on the width dimension of the workpiece W, the top die 41F, 4
In order to change the length dimension of 1R, the top die 41F,
41R is supported by the ram 27 so as to be movable and fixed in the left-right direction. In addition, on the appropriate side frame 7,
Top die 41F.

A rack device 75 equipped with a plurality of mold storage parts capable of storing 41R is installed.

Although the details of the rack device 75 will be omitted, it provides a predetermined top die according to the width of the workpiece (it has a mold storage section that stores predetermined top dies in multiple stages in the front and rear).

Front and rear top dies 41F supported on the front and rear of ram 27
, 41R at the same time, mold changing devices 77F are provided on the front and rear surfaces of the ram 27, respectively.

77R is provided. More specifically, guide rails 7 extending in the left and right directions are provided on the front and rear surfaces of the ram 27, respectively.
9F and 79R are installed, and this guide rail 79F
, 79R, mold changing devices 77F and 77R are movably supported, respectively.

In order to move the mold changing devices 77F and 77R in the left and right direction along the guide rails 79F and 79R, the ram 27
Pulleys 81 (the rear pulleys are not shown) are rotatably supported near the left and right side portions of the front and rear surfaces, respectively. A belt 83 such as a timing belt is wound around each pulley 81, and mold changing devices 77F and 77R are connected to each belt 83, respectively. on the other hand,
The pulley 81 has a through shaft 8 that passes through the ram 27 in the front-rear direction.
The through shaft 85 is operatively connected to a control motor M2, such as a servo motor or a pulse motor, mounted on the ram 27 via a bracket 1-87.

With the above configuration, by rotating the control motor 187, the front and rear molds can be exchanged f! The Xl devices 77F and 77R move simultaneously in the left and right directions along the guide rails 79F and 79R.

Referring to FIGS. 3 and 4, the mold changing device 77F
(77R), the guide rail 79F1. :
A moving block 87, which is movable in the left and right directions along the belt, is connected to the belt 83 via a suitable connector 89.

The moving block 87 has a through hole 7 bored in the frame 7.
Eight nose portions are formed that can penetrate H and protrude toward the rack device 75 side, and a guide rail 91 that is parallel to the moving direction of the moving block 87 is formed on the nose portion 89 . A slide member 95 having a mini-cylinder 83 supported at its tip is movably supported on the guide rail 91. This slide member 95 is connected to the moving block 8
Piston rod 9 of retraction cylinder 97 supported on 7
It is connected to 7R.

Therefore, by appropriately operating the retraction cylinder 97, the slide member 95 is reciprocated with respect to the moving block 87.

As shown in FIG. 4, the mini-cylinder 93 includes a piston rod 93R that can be freely engaged with and disengaged from an engagement hole 41H formed on the front side of each divided piece in the top die 41F. A rectangular notch 41N long in the left-right direction is formed on the front side surface of the top die 41F, and the top die 41F is supported by engaging the notch 41N with a support bar 99. The support bar 99 supports the ram 27
It extends in the longitudinal direction and is supported by a support member 101 fixed to the lower surface of the ram 27 via a plurality of bolts 103 and a spring 105 such as a coil spring.

A stepped portion 418 and an inclined portion 41B are formed on the rear side surface of the top die 41F. The stepped portion 413 of the top die 41F is supported by a support bar 107 provided on the ram 27 in parallel with the support bar 99, and the inclined portion 41B is supported by a clamp provided at an appropriate number of locations on the ram 27 so as to be movable up and down. Inclined portion 10 formed on member 109
It is in contact with 9B. □The Franz member 109 is connected to the piston rod 111R in the clamping cylinder 111 of the top die 41F mounted on the ram 27.

The clamping force acting on the inclined portion 41B of the top die 41F is to press leftward in FIG. Since they are in the same direction, the fixation of the top die 41F will not loosen during the bending process, and the clamping force of the top die 41F may be small.

With the above configuration, by engaging the piston rod 93R in the mini cylinder 93 with the engagement hole 41H of the top die 41F and moving the movable button 87, the top die 41
F can be moved and the top die 41 replaced.

At this time, the operation of the retraction cylinder 97 and the movement block 87
By performing this positioning, the top die 41F having an appropriate length depending on the width of the workpiece can be moved toward the ram 27 side.

The bending machine 1 having the above configuration is located at the -E section of the ram 27, and connects the bottom die 21F to the tube dies 41F and 41R via the movable blocks 45F and 45R.

Pressing cylinders 43F and 43R, which press in the direction 21R, are on the right. Also, a lifting cylinder 31 that drives the ram 27 up and down, bending cylinders 61F and 61R1 that move the bend beams 47F and 47R up and down, and a mini cylinder 93.
Furthermore, it has a clamping cylinder 111 for clamping the top die.

FIG. 5 shows an embodiment of a hydraulic circuit for operating these cylinders.

The hydraulic circuit 113 includes three oil pumps PL1. PL2. It has PH.

Each pump PL1. PL2. PH pumps up the oil in the oil tank OT and passes it through the oil path 011. Supply pressure oil to O12 and O12.

A check valve CVI is provided in the oil passage OL1, and a relief valve 5OLI with a solenoid valve is connected between the oil pump PLI and the check valve CV1. Further, a solenoid valve 5QL2 is provided in the oil passage ○L2, and a solenoid valve relief valve 5OL3 is connected between this solenoid valve 5QL2 and the oil pump PL2. Furthermore, oil path 01
3 is provided with an electromagnetic valve 5OL4, and an electromagnetic proportional valve DR is connected between this electromagnetic valve 5OL4 and the oil pump PH.

The check valve CV1 and the electromagnetic valve 5OL2 are connected to an oil path OL4. And is this oil passage OL4 for switching up and down? 1 [Connected to the lifting cylinder 31 via the valve 5OL5. The two lifting cylinders 31 have their supply and discharge ports connected in parallel, and a balance valve BV is provided in the blood line connected by 1g to the cylinder oil discharge side. The oil passage ○L4 is connected to bending cylinders 61F and 61R via electromagnetic valves 5OL6 and 5OL7 for switching up and down. The oil pressure of the oil passage ○L4 is controlled by the solenoid valve 5QL2 to the oil passage OLI or the oil passage O.
Switching control is possible with that of L2. As described above, it is possible to supply pressure oil from the oil path OL1 or OLL to the lifting cylinder 31 and the bending cylinder 61F (61R).

Oil road 0. The solenoid valve 5OL4 installed in L3 is oil path 0.
15, and this oil passage OL5 is connected to check valve CV
It is connected to the oil passage OL4 via 2. Oil road office lady
When the oil pressure in No. 5 decreases, oil is supplied to the oil passage OL5 from the oil passage OL4 via the check valve CV2.

The oil passage OL5 has solenoid valves 5OLa, 5OLb, 5O.
The pressing cylinders 43F and 43R are connected via Lc..., the clamping cylinder 111 is connected via a solenoid valve 5PL8, and further the mini cylinder 93 is connected via a solenoid valve 5OL9.

The solenoid valves 5OLa, 5OLb, and 5OLe are used to control the switching of the pair of front and rear press cylinders 43F and 43R.

With the configuration of the hydraulic circuit as described above, the lifting cylinder 31
, and the bending cylinders 61F and 61R are operated by being supplied with pressure oil from the oil passage 011 or the oil passage OL2.

Also, a pressing cylinder 43F.

43R, the clamp cylinders 111F, 111R1, and the mini cylinder 93 are supplied with pressure oil from the oil path OL3 and are operated. However, oil path OL4 and oil path 01
Since a check valve CV2 is provided between the oil passage OL5 and the oil passage OL5, when a large amount of pressure oil is used, for example, when a large number of pressure cylinders 43F or 43F operate simultaneously, the oil passage OL5 is temporarily closed. In some cases, pressure oil is supplied from oil passage OL4. Note that the hydraulic circuit 113 includes a pressure gauge PG.
or pressure switch PSW1. PSW2. Although PSW3 etc. are provided, these are provided as appropriate.

FIG. 6 is a block diagram of the configuration of the pressure cylinder control circuit.

The pressure cylinder control circuit 115 includes an NC data management module 117, a pressure force operation module 119, a pressure cylinder selection module 121, an execution module 123.
125.

NC data management module 117 is manual input, N
C tape input and other NC data through communication from a central control unit (not shown) are input, and the plate thickness T1 material (tensile strength) S and bending width history of the workpiece W are read from the input data contents.

The pressing force calculation module 119 calculates the bottom dies 21F, 21R and the top dies 41F, 4 based on the plate thickness T and material S.
The pressing force between 1R, in other words, the pressing cylinder 43F,
Calculate the optimum value P of the pressing force of 43R. This optimal value P
As shown in the conventional example, bend beams 47F, 47
It is determined so that the product accuracy is good, taking into account the amount of workpiece retraction caused by the action of R and the deflection of the frame.

The pressure cylinder selection module 121 selects a predetermined pressure cylinder 43F, 43R depending on the bending width, and outputs a pressure cylinder selection signal Se.

The execution module 123 inputs the optimum pressing force P from the pressing force calculation module 119, and outputs a predetermined current I according to this value.

This current ■ is, for example, a 5-stage channel CHI.

This can be done by selecting CH2, . . . CH5.

The output current is output to the electromagnetic proportional valve DR.

The execution module 125 is the pressing cylinder selection module 1
Input the selection signal SO from 21, and select a large number of solenoid valves 5OL.
Only a predetermined solenoid valve of the a-8OLe is operated.

In the hydraulic circuit 113 equipped with the pressure cylinder control circuit 115 configured as described above, it is possible to operate only the necessary pressure cylinders 43F and 43R with the optimum pressing force depending on the workpiece thickness T, material 81 bending width, and more. , This makes it possible to form an optimal holding state.

[Effects of the Invention] The present invention relates to a bending device that can optimally control the pressing force between a bottom die and a top die. Therefore, in the bending machine according to the present invention, it is possible to press and support the workpiece with the optimum pressing force and apply the bending beam, and the workpiece is pulled in an amount greater than a predetermined amount. In addition, the fixed frame is not bent more than a predetermined amount, and the product accuracy can be improved.

[BRIEF DESCRIPTION OF THE DRAWINGS] FIG. 1 is a front view of a bending device embodying the present invention;
Figure 2 is a side sectional view taken along the line ■-■ in Figure 1, Figure 3 is an enlarged side view of the part marked by the arrow ■ in Figure 2, and Figure 4
The figure is an explanatory side cross-sectional view taken along the line IV-IV in Fig. 3, Fig. 5 is an explanatory view of the hydraulic circuit, and Fig. 6 is an explanatory diagram of the press cylinder control circuit that controls the press cylinder part of this hydraulic circuit. It is a block explanatory diagram. 1... Bending machine 21F, 21R... Bottom die 31... Lifting cylinder 41F, 41R... Top die 43F, 43R... Pressing cylinder 47F, 47R... Bend beam 61F, 61R... ...Bending cylinder 93...Mini cylinder 111F, 111R...Clamping cylinder 117...
...NC data management module 119...Press force calculation module 121...Press cylinder selection module 123.12
5...Execution module OR...Solenoid proportional valve■...Plate thickness S...Material (tensile strength)...Bending width Fig. 1 Fig. 2 Fig. 3 Fig. 4

Claims (2)

[Claims] (1) A bottom die and a top die that protrude a workpiece of a predetermined width by a predetermined amount and press and support it with a predetermined pressing force;
a bend beam that bends the protruding portion of the workpiece by moving along the protruding surfaces of the bottom die and the top die in a direction perpendicular to the work screw;
Comprised of a calculation means for calculating the pressure support force according to the type of work of bending processing, and a pressure support force providing means for applying the pressure support force calculated by the calculation means to the bottom die and the top die. Bending processing machine. (2) The bending machine according to claim 1, wherein the type of work of the bending process is determined according to the type of workpiece, that is, the bending width, material, and plate thickness.