JPH04111995A - Double action press device - Google Patents

Abstract

PURPOSE:To allow the setting of the min. ram stroke length with respect to a required drawing depth and to allow the press to withstand blank holding force of a large load by vertically driving at least one piece of ram of two pieces of the rams by means of a specific link motion mechanism. CONSTITUTION:The one lower ram 15 of the rams 5, 15 moving back and forth is vertically moved by the link motion mechanism. The 2nd link 25 of this link motion mechanism is fitted freely oscillatably by a pivot pin 24 to a frame. The link motion mechanism, therefore, has a toggle effect and can yield large force in the vicinity of its top dead point. Then, the press device is capable of withstanding the large blank holding load without increasing the rigidity and mass of the device itself. Arbitrary dwelling at about the top dead point is possible when the ram is vertically moved by the link motion mechanism. The ram is displaced under optimum conditions by properly adjusting a lever ratio, etc.

Description

Detailed Description of the Invention (Field of Industrial Application) The present invention is suitable for press equipment, particularly for forming deep-drawn containers such as thin-walled beverage cans, which require long strokes, strong pressure, and high speed. This invention relates to a double action press device.

(Prior Art) Conventionally, for example, a press device that forms two-piece cans such as thin-walled beverage cans by deep drawing has a die fixed to a table, and a wrinkle presser that moves up and down in opposition to the ram. It is a double-action press that has a blanking ram attached to it and a draw ram to which a punch is attached.The workpiece is fed to the die on the table, and the wrinkle presser is lowered onto the workpiece to remove the workpiece. As the outer circumference of the object is pressed, the punch descends to draw the object.

When the ram rises after the drawing process is finished, in the case of a drawing-through die, the workpiece is removed from the tool by a stripper. If the die is not a draw-through die, the knockout protrudes after forming to separate the object from the tool and move it to the ejection position. In addition, as another type, a so-called opposed ram type double action press device is known, in which a die mount and a punch both face each other and move up and down.

(Problems to be Solved by the Invention) In recent years, from the viewpoints of resource saving and high efficiency, there has been a demand for thinner cans and faster molding processes. However, in the forming process of deep drawn cans, the long stroke and thin wall require strong pressure to suppress wrinkles, which exceeds the forming pressure. Conventional press equipment has the following problems and cannot meet this demand. However, it is still not enough.

a. When the ram moves in one direction, the workpiece must be fed and discharged only after the ram has moved at least the height of the workpiece from the supply and discharge reference plane. The stroke of the ram must be increased for discharge, making it difficult to increase speed.

b. Since the ram vertical movement mechanism is a crank mechanism, its displacement curve is a sine curve, and extra cushioning (work) is required at the top dead center or bottom dead center position. Also, it is difficult to change the stroke of the ram.

The thinner the C0 material is, the more likely it is to wrinkle, so a strong crease-holding force is required.In order to obtain a stable and strong crease-holding force, the rigidity and weight of the device must be increased to withstand a large load. In addition, since a vibration device that generates a large torque is required, the device becomes large in size, and the excitation force becomes large, causing vibration pollution.

d. The discharge of the workpiece after forming is performed by operating the knockout after the movement of the punch, so it takes time to discharge the workpiece.

e. In conventional devices, each ram is supported and guided by an individual guide post, so the number of guide posts is large (usually 8).
, which requires a large installation space.

The present invention was devised in order to solve the above two problems, and it is possible to minimize the ram stroke length for the required drawing depth and to withstand the wrinkle pressing force of a large load. can be used without the need for extra cushioning.
Another object of the present invention is to provide a double-action press device that can save space by reducing the number of ram guide posts, reduce the excitation force of the press, and enable high-speed operation. shall be.

(Means for Solving the Problems) A double action press device of the present invention that solves the above problems includes: a first link connected to a double vertically moving slide in which two rams move vertically; A second link whose one end is connected to the frame and whose middle part is swingably attached to a pivot pin that projects from the frame; and a third link whose one end is swingably connected to the other end of the second link. It has a structure characterized by being driven up and down by a link motion mechanism.

The double action press device has two rams arranged so that they both move up and down in one direction with respect to a reference surface for supplying and discharging the to-be-formed material, and two rams that are arranged facing each other so that they move up and down in opposite directions. It may be something that Further, the ram that is vertically driven by the link motion mechanism is disposed below the molded product supply/discharge surface, and is fitted to a guide post of the ram disposed above so as to be vertically movable,
The number of guide posts is reduced by using the guide post of the ram located above as the guide post of the ram located below.

Furthermore, a die is attached to the lower ram and a forming punch is attached to the upper ram, and a knockout is provided upright on the bed, and a hole for passing the knockout is formed in the lower ram. By moving up and down, the knockout moves relatively into and out of the die and discharges the molded object after molding, thereby shortening the discharge time.

It consists of a rotating main shaft bearing on a frame, a sub-crankshaft that rotates with the rotating main shaft by gear transmission, and a balance weight suspended from the sub-crank shaft via a connecting rod, and the meshing ratio of the gear transmission and the sub-crankshaft are A dynamic balancer device is provided which can adjust the vibration phase of the balance weight by appropriately selecting the length ratio of the crank lever of the crankshaft and the connecting rod, thereby reducing the excitation force.

(Function) One of the reciprocating rams 11 moves up and down by a link motion mechanism. In this link motion mechanism, the second link is pivotally attached to the frame with a pivot pin, so the link motion mechanism has a toggle effect and can obtain a large force near the top dead center. . Therefore, it is possible to withstand a large wrinkle pressing load without increasing the rigidity or mass of the device itself. =7 By moving the ram up and down with the link motion mechanism, it is possible to arbitrarily take a dwell near the top dead center, and by adjusting the lever ratio etc. as appropriate, the ram can be displaced under optimal conditions. There is no need to provide a cushion unlike a normal ram that moves in a sine curve.

In addition, by arranging two rams facing each other, moving the lower ram up and down with the above-mentioned link motion mechanism, and moving the other ram up and down with a normal up-and-down mechanism, such as a crank mechanism, the ram can be moved up and down by the link motion mechanism. can also be used as a guide post for the upper ram without providing a separate guide post. By moving the rams in opposite directions, the relative speed between the rams is twice that of a one-way ram, and when the lower ram descends, it naturally hits the knockout attached to the bed. Since the molded product is supported and can be taken out in that state, the time required to feed and discharge the molded product can be shortened and the speed can be increased.

The dynamic balancer device built into the press device transmits the rotation of the crankshaft of the press device to the sub-crankshaft at a predetermined speed ratio through a gear mechanism as the crankshaft of the press device rotates. The balance weight suspended from the lower end of the connecting rod fitted to the is moved up and down. Therefore, by displacing the balance weight in a phase opposite to the phase of the reciprocating load of the device, the excitation forces act in opposite directions, making it possible to reduce the excitation forces. The displacement phase of the balance weight can be adjusted by appropriately selecting the meshing ratio of the gear transmission and the length ratio of the crank lever and the connecting rod of the sub-crankshaft.

(Example) Embodiments of the present invention will be described in detail below based on the drawings.

FIGS. 1 to 5 show an example of an opposed lambda pull action press, and FIG. 1 is a schematic front view showing the whole, and the partial details are shown in FIGS. 2 to 5. This will be explained based on FIG. 1 and with reference to FIGS. 2 to 5.

In the figure, reference numeral 1 denotes a base, with a bed 2 above the base, an upper frame (crown) 3 above the base, which is fixedly supported by tie rods 4, and appropriate panels are attached to form the frame. There is. 5 is the upper ram to which the punch 6 for deep drawing is attached, details of which are shown in the second section.
As shown in FIG. 3, the upper ram 5
is fixed to the upper end of a guide post 9 which moves up and down by fitting its four corners into guide bushes 7.8 fixed to the frame so as to be able to move up and down. The lower ends of the guide posts 9 are connected to each other by two crossheads 10, and the intermediate portions of the crossheads are connected to a crankshaft 11 via a connecting rod 12.

Reference numeral 15 designates a lower ram for pressing down to which a die 16 for deep drawing is attached, and lower ram guide bushes 17 that fit into the guide posts 9 and move up and down are fixed to the four corners of the lower ram. It is guided by the guide post 9 via the bush and moves up and down. Therefore, the guide post 9 serves both as a guide for the upper ram and a guide for the lower ram, and there is no need to provide separate guide posts as in the prior art, so the number of guide posts 1 can be reduced by half.

The lower ram 15 is moved up and down by a link motion mechanism, the details of which are shown in FIG.

In the figure, a slide 20 is connected to the crankshaft 11 via a connecting rod 21, and is guided by a slide guide 22 fixed to the frame and moves up and down as the crankshaft rotates. The first arm 2 is symmetrically attached to the slide 20.
A second arm 25 is rotatably attached to the other end of the first arm 23, and the other end of the second arm 25 is rotatably attached to a pivot pin 24 that projects from the frame. A third arm 26 connected to the lower ram 15 is connected to be rotatable in sequence, thereby forming a link motion mechanism. Therefore, the lower ram has a toggle mechanism, and the crankshaft 1
1 rotates and the second arm 25 rotates around the pivot pin, even if a large load acts on the lower ram, the force is received by the pivot pin, so the high load state can be maintained at top dead center.

That is, it is possible to withstand a large load while reducing the torque burden on the immediate action system. In addition, by adopting the above-mentioned link motion mechanism, the displacement of the lower ram can be made to dwell for an appropriate length of time at the top dead center, as shown in Figure 5, so that the displacement of the lower ram follows the sine curve shape of the conventional crank mechanism. There is no need for extra work as in the case of

The displacement curve of the lower ram can be optimally selected by combining the length and arrangement of each arm.

A punch plate 30 is attached to the upper ram 5, and a punch 6 is fixed to the lower surface of the punch plate. 31 is an upper die shoe fixed to the upper frame 3;
A redraw sleeve 3 that holds the molded product between its lower end and the upper surface of the die, corresponding to the position where the punch 6 penetrates.
2 is retained. Reference numeral 33 denotes a presser cylinder that presses the upper surface of the flange of the redraw sleeve 32. In this embodiment, a nitrogen cylinder is used to stably maintain a high pressurizing force and securely clamp the flange portion of the molded product. I made it possible.

A lower die shoe 34 fixes the die 16, and is fixed to the lower ram 15. 35 is a knockout installed on the base 1 so as to be able to penetrate the lower ram, die shoe, and die.

On the other hand, since a link mechanism is used as the vertical movement mechanism of the ram, a complicated excitation force curve unique to the link mechanism is generated in the press equipment, and there is a problem that vibration increases when operating at high speed. In this example, by driving the balance weight with a waveform corresponding to the excitation force curve, the excitation force is reduced as much as possible, making it possible to cope with higher speeds.

40 is a dynamic balancer device provided for this purpose, the details of which are shown in FIG.

The dynamic balancer device of this embodiment has sub-crankshafts 42.4 at symmetrical positions with respect to the crankshaft 11 as the center.
3, and a balance weight 46 is suspended from the sub-crankshaft via connecting rods 44 and 45. The transmission mechanism employs a gear mechanism shown in FIG.
The power is transmitted in the following order: driven gear 49 - sub-crankshaft 42 - sub-crankshaft gear 50 - crankshaft gear 51 - idle gear 52 - idle shaft 53 - sub-crankshaft gear 54 - sub-crankshaft 43. Said sub-crankshaft gear 50.
54 and the idle shaft gear 52 have the same number of teeth, so that the sub-crankshafts 42 and 43 rotate at the same rotation speed and in opposite directions. A similar mechanism is provided at the other end of each shaft, as shown in FIG.

Therefore, the balance weight 46 is attached to the sub-crankshaft 42.
43, the left and right connecting rods 44. in FIG.
45, the vertical components have vectors of the same magnitude and in the same direction, but the horizontal components have vectors of the same magnitude and opposite directions, so the horizontal components are canceled out and the dynamic weight is The dynamic balancer can move vertically up and down without intentionally providing a vertical guide.

In addition, in Fig. 1, 60.61 is the air spring for static load balance of the upper ram 5, and 62.63 is the lower ram 15.
This is an air spring for static load balance. Further, 64 is a drive shaft of a transfer finger for carrying the molded product into and out of the die, and swings back and forth. 65 is an oil pan.

The press apparatus of this embodiment is constructed as described above, and the sixth
The operation will be explained with reference to FIGS.

As the crankshaft rotates, the upper ram 5 and the lower ram 15 are displaced in a sine curve shape as a whole by the crank mechanism as shown by the curve (a), and the lower ram 15 is a combination of the crank and the link mechanism. As a result, as shown by the curve (b) in FIG. 7, there is a dwell near the top dead center, and the displacement is in the form of a sine curve at the bottom dead center. Note that (C) is the feed reference line.

Now, in FIG. 1, the molded product, which has been previously narrowed to a shallow depth in the previous step, is conveyed to the position of the die 16 by a conveyor (not shown) arranged at the A-A level, and is supplied to the ascending path of the die by a transfer finger. . At that time, the upper ram 5 is at the position where it has started descending from the top dead center, and the lower ram 15 is rising from the bottom dead center toward the top dead center (
(See Figure 6(a) and Figure 7(a) locations). Next, as the crankshaft 11 rotates, the lower ram 15 is guided by the guide post 9 supporting the upper ram and further raised by the link mechanism shown in FIG. The lidro sleeve 32 is supported and raised, and the lidro sleeve 32
The die 16 and the draw sleeve 32 press and hold the inner circumference of the bottom wall of the molded object to suppress wrinkles. From then on, the wrinkle suppression is continued until the end of molding (6th
(See Figure (b) and Figure 7 (b) position). At this time, the upper flange of the redraw sleeve comes into contact with the lower end of the rond of the wrinkle-pressing nitrogen cylinder and is slightly cushioned, but the pressure can be controlled as appropriate by appropriately controlling the operating pressure of the cylinder. In particular, in this example,
Since a nitrogen cylinder is used as the cylinder, a high working pressure can be obtained, and it is possible to strongly suppress wrinkles, and stable molding can be performed even when the drawing ratio is large.

At the same time, the upper ram is lowered by the rotation of the crank 11 and the guide post 9 is lowered via the crosshead, and the punch attached to the upper ram is lowered to form the object held on the upper surface of the die. that time,
Since both the lower ram and the upper ram move toward each other, the forming speed is also much faster than in the case of a unidirectional double-acting ram. Deep drawing is performed until the crankshaft 11 rotates 180 degrees to complete drawing to a predetermined depth and thinning. In this example, as shown in the figure, the molding is carried out with a flange, and when the molding is completed, the flange is held between the die top face draw sleeve (FIG. 7(C), No. 7 Figure (c)
reference)). The drawing depth can be adjusted as appropriate by selecting and replacing the tip head member, punch head member, and redraw sleeve of the knockout with appropriate lengths. Therefore, by setting and transferring a plurality of sets of dies and punches so that the depth of drawing increases sequentially through the same movement, a series of steps can be automatically performed by one device.

When forming is completed and the crank rotation starts in the backward stroke, the lower ram descends and the upper ram simultaneously rises, so that the formed workpiece separates from the die 16, redraw sleeve 32 and punch head and enters the space. The bottom wall is supported by the knock ring 1 at 35 (see FIG. 6(d) and FIG. 7(d)).

In this state, the transfer finger drive shaft swings, and the transfer finger takes out the molded product from the knockout and transports it to the next process. Therefore, in the apparatus of this embodiment, the knockout relatively takes out the molded object from the die during the lowering or ascending stroke of the lower ram and upper ram, and there is no need for the moving time of the knockout as in the conventional case. As soon as a space in which the object to be formed can move is secured while the upper ram and lower ram are moving, the object to be formed can be discharged, so that the cycle can be shortened and the speed can be increased.

In the above-mentioned double action press, the upper ram 5 and the lower ram 15 move up and down to generate excitation forces having waveforms (d) and (e) as shown in FIG. 8, respectively. Therefore, the excitation force resulting from the combination of both is the broken line curve (
As shown in f), in this diagram, the vertical axis represents the downward excitation force upward from the center line, and the upward excitation force downward. Therefore, in this embodiment, the gear ratio is set so that the rotation ratio of the crankshaft 11 and the sub-crankshaft 42, 43 is ]:2 so that the balance weight 46 vibrates twice as many cycles as each of the above-mentioned rams. By the vibration of the balance weight 46, a dynamic load having a waveform (g) shown in FIG. 9 is obtained. Therefore, the overall excitation force after being balanced with the ram composite excitation force becomes the curve (h) in the figure, and the overall excitation force could be considerably reduced.

As in this embodiment, by configuring the dynamic balancer with a gear mechanism, the phase of the excitation force due to the balance weight can be adjusted by appropriately changing the ratio of the number of teeth and the ratio of the arm length of the sub-crank to the connecting rod length. It can be adjusted as appropriate. Furthermore, since the magnitude of the excitation force can be adjusted arbitrarily by adjusting the mass of the balance weight, it is possible to easily obtain a dynamic balancer with a waveform that balances the excitation forces of both rams. Vibration of the press equipment can be reduced.

Although the preferred embodiments of the present invention have been described above, it goes without saying that the basic technical means of the present invention is not limited to the opposed ram press as described above, but can also be applied to a one-way lambda pull action press.

10 to 12 show an embodiment for a one-way lambda pull action press. The explanation of the parts common to the previous embodiment will be omitted as much as possible, and only the characteristic points will be explained.

In the figure, 70 is a draw ram to which a punch is attached, which corresponds to the upper ram in the above embodiment, and is supported by the draw ram guide post 1-71, and is actively moved up and down by a crank mechanism like the upper ram in the above embodiment. be done. Reference numeral 72 denotes a blanking ram to which a wrinkle presser is attached, which corresponds to the lower ram of the embodiment described above, and is attached to a blanking ram guide post 73. Draw ram guide post 71 and ranking ram guide post 7
3 is the upper guy I attached to the frame body, respectively.
Button 74.76 and lower guide button 75.7
7 so that it can move up and down.

As shown in FIG. 11, the lower end of the blanking ram guide post 73 is connected to a crosshead 78 that connects the left and right link mechanisms, and the blanking ram can be moved up and down by the link mechanism in the same way as the lower ram in the previous embodiment. be done.

That is, in FIG. 11, 79 is a crankshaft, and the rotation of the crankshaft is converted into the vertical movement of the slide 81 via the connecting rod 80, and the downward movement of the slide is converted into the vertical movement of the slide 81.
, a second arm 84, a third arm 85, whose intermediate portion is rotatably attached to a pivot pin 83 protruding from the frame;
This is converted into vertical movement of the blanking column 72 via a crosshead 78. Therefore, the displacement of the blanking ram can be freely changed by adjusting the length of each link, and an appropriate dwell can be secured near the bottom dead center, eliminating the need to provide an extra cushion. Also, the toggle action allows you to obtain strong pressing force.

(Effects) The present invention has the above-described configuration and provides the following special effects.

One ram is driven by a link motion mechanism, so
It can have a toggle effect, can withstand a large wrinkle presser load, and can enable high-speed deep drawing of thin-walled materials without increasing the size of the device. Also,
By appropriately selecting the combination of the length and arrangement of each arm of the link motion mechanism, the ram can be displaced with an optimal displacement curve for molding. Furthermore, since the dwell can be removed near the top dead center or bottom dead center, extra cushioning is no longer necessary.

By using the opposed ram method, the ram stroke length can be minimized for the required drawing depth, and since each ram is retracted in the opposite direction after forming, there is no need for knockout movement time. Since the object to be formed can be discharged, even in deep drawing that requires a long stroke, it is possible to shorten the cycle and increase the speed.

Furthermore, according to the structure of claim 4, since the guide posts 1 to 1 of the upper ram are also used as the guide posts of the lower ram, the number of guide posts can be reduced to half of the conventional number, and the vertically moving load can be reduced. This is advantageous in speeding up the process and also allows for space saving.

Furthermore, according to the structure of claim 6, by providing a dynamic balancer device that displaces the balance weight by a gear mechanism, it is possible to easily obtain a dynamic balancer having a waveform that balances the excitation forces of both rams. This can effectively reduce the excitation force of the press device and enable high-speed operation.

[Brief explanation of the drawing]

The drawings show an embodiment of the double action press device according to the present invention, and FIG. 1 is a front view of the double action press;
Figure 2 is a schematic front view of the main part, Figure 3 is a schematic cross-sectional view taken along line A-A in Figure 2, Figure 4 is a schematic cross-sectional view taken along line B-B in Figure 2, and Figure 5 is a front view of the dynamic balancer device. Figure, Figure 6(a)
thru (d) are main part sectional views showing the molding process! Figure 7 is a displacement diagram of the ram in the device of the above embodiment, Figures 8 and 9.
The figure is a line diagram showing the excitation force in the above device, Figure 10 is a schematic diagram of the front main part of a double action press with a one-sided ram, which is another embodiment, and Figure 11 is a cross-sectional view taken along line C-C in Figure 10. It is. 1: Base 2: Bed 3: Upper frame (crown) 5 Near frame 6: Punch 7.8
Ni guide post 9 Ni guide post 10: Cross head 11.75: Crank shirt 1- 12.
21: Connecting rod 15: Lower ram 16: Die 1
7: Lower ram guide push 20 Ni Ride 23:
1st arm 24: Pivot pin 25: 2nd arm
26: Third arm 30: Punch plate 31 Near sleeve die shoe 32: Redraw sleeve 33
: Wrinkle holding cylinder 35: Knockout 40: Dynamic balancer device 42.43: Sub crankshaft 46: Balance way 1- 4.7: Driving shaft
48: Drive gear 49: Transmission gear 50.54: Sub crankshaft gear 51: Main crankshaft gear 52:
Idle gear 53: Idle shaft 70 nitro ram
72 Nibrankrum Patent Applicant Toyo Seikan Co., Ltd. Applicant Agent Patent Attorney Fumio Sato (and 2 others) (a) (b) Figure (c) (d) Figure Procedure Amendment (Voluntary) Heisei September 27, 2018

Claims (1)

[Scope of Claims] 1) A double action press in which two rams move up and down, and at least one of the two rams is a slide that moves up and down from a crankshaft via a connecting rod. A first link connected to the first link, a second link having one end connected to the first link and pivotally attached to a pivot pin having an intermediate portion protruding from the frame, and one end connected to the other end of the second link. A double action press device characterized in that the double action press device is driven up and down by a link motion mechanism consisting of a third link that is swingably connected. 2) The double action press apparatus according to claim 1, wherein both of the two rams are arranged to move up and down in one direction with respect to a reference surface for supplying and discharging a molded material. 3) The double action press apparatus according to claim 1, wherein the two rams are arranged to face each other so as to move up and down in opposite directions with respect to the material supply/discharge surface. 4) The ram that is vertically driven by the link motion mechanism is a ram that is placed below the molded material supply/discharge surface, and a guide that supports the ram that is placed above and moves up and down with respect to the frame. 4. The double action press device according to claim 3, wherein the post is fitted in a vertically movable manner so that the guide post of the ram disposed above also serves as the guide post of the ram disposed below. 5) A die is attached to the lower ram, a forming punch is attached to the upper ram, and a knockout is erected on the bed, and a hole is formed in the lower ram for the knockout to pass through. Claim 3, wherein the knockout moves relatively into and out of the die by vertical movement of the ram, and discharges the molded object after molding.
Or the double action press device according to 4. 6) Consisting of a rotating main shaft bearing on a frame, a sub-crankshaft that rotates with the rotating main shaft by gear transmission, and a balance weight suspended from the sub-crank shaft via a connecting rod, the meshing ratio of the gear transmission and the sub-crankshaft are The double action press device according to any one of claims 1 to 5, further comprising a dynamic balancer device capable of adjusting the vibration phase of the balance weight by appropriately selecting a length ratio between the crank lever and the connecting rod of the crankshaft. .