JP2008229733A - Shear press machine capable of shearing in high speed - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compact press machine capable of shearing in high speed. <P>SOLUTION: The press machine is equipped with a driving cylinder device with a large projected net area and a slave cylinder device with a small projected net area on a slide side so that they can move up/down synchronously, and in addition, a shearing part (fixed blade and mobile blade) on a bolster side. The machine is formed in such a structure that a working fluid in a lower chamber of the slave cylinder device can be discharged outside while the working fluid flows into an upper chamber of the slave cylinder device from an upper chamber of the driving cylinder device and also the working fluid can be supplied into the lower chamber of the slave cylinder device from the outside while the working fluid flows back from the upper chamber of the slave cylinder device to the upper chamber of the driving cylinder device. After a driving pin of the driving cylinder device comes into contact with the bolster side and restricted in this position while the slide is moving down, the mobile blade is quickly lowered by a driven pin. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a press machine capable of performing shearing at a high speed with an increased slide speed.

  In general, the speed of a press machine having a large stroke (long) is low due to inherent circumstances in structure and function. In the press machine, the stroke becomes smaller (shorter) as the speed increases. Even if the stroke is made small, it is often difficult to increase the speed due to the problems related to the consistency of the cycle time of press working and work loading / unloading. In other words, there is no large stroke and high speed press machine.

  The relationship between the press working mode and the accuracy / quality of the product is close. When press processing (for example, plastic processing such as drawing) is performed on a single material (blank), it is preferable to reduce the slide speed. However, in the case of shearing, the higher the shear rate, the better (excellent) the finishing accuracy and quality of the shear cross section.

  Thus, conventionally, in addition to a press machine that can be said to share a relatively low speed operation (press processing), there are many cases where a dedicated shearing device that shares a relatively high speed operation (shear processing) is employed. . That is, a single material (blank) is created by shearing a continuous material, for example, by using a shear processing device. After that, using a press machine, the single material (blank) supplied and set is pressed to produce a product (single material).

  A conventional shear processing apparatus has a structure in which shearing is performed by moving a moving blade relative to a fixed blade. Further, in many cases, a driving source (for example, a main motor or a main shaft) mounted on a press machine (in the crown) is used as the power of the shear processing dedicated device. Specifically, a complicated power transmission mechanism (gear train, connecting rod, cam drive unit, cam, etc.) must be interposed between the drive source and the moving blade drive shaft.

  However, when the drive source of the press machine is used, it is difficult to increase the shearing speed. Rather, there are many cases where the speed becomes much lower than the normal slide speed (average slide speed) as in the case of switching to the trial driving operation. Therefore, in terms of shearing, accuracy and quality are inferior (burrs, scratches, scratches, etc. occur).

  As measures for solving this problem, an apparatus (Patent Document 1) with an additional grooving mechanism and an apparatus (Patent Document 2) provided with a sub drive source different from the drive source of a press machine have been proposed.

  The proposed former device (grooving mechanism) includes a sliding body 22, a reduction claw body 30, a rotation support body 28, a pushing body 29, a cylinder 32, and the like, and a radius of the rolling roll 19 for grooving having a convex portion 19a. The chamfering groove A1 having an arbitrary depth is rolled in advance on the outer periphery of the sheared portion of the continuous material (pipe A). That is, from the viewpoint of improving quality while giving up speeding up, it is a concept of performing preforming (rolling) prior to shearing.

The proposed latter device is a material cutting device 10 (including a drive unit 14, an engagement pin 15, a cam plate driving body 16 and the like) driven using a drive source (main motor 6), and a drive source (6). A sub-drive mechanism (including the sub-drive source 20) that enables the cutter 13 to be driven at high speed with priority is provided. In other words, from the viewpoint of increasing the speed without depending on the press machine side, the idea is to add a sub-drive mechanism that is close to the press machine but is irrelevant to the press machine (drive source).
JP 2004-249448 A JP 2003-220443 A

  Each of the proposed devices becomes more complex and large as the drive structure is doubled compared to the conventional shear processing dedicated device, meeting the demands for universal downsizing and cost reduction. I can't. It also causes a significant increase in equipment costs. Moreover, in the actual operation, the degree of speeding up is low for increasing the complexity, size, and cost of the device.

  An object of the present invention is to provide a compact press machine capable of performing high-speed shearing.

  According to the first aspect of the present invention, a drive cylinder device having a large pressure receiving area and a driven cylinder device having a small pressure receiving area are mounted on the slide side so as to be able to move up and down synchronously with the slide, and the moving blade is relative to the fixed blade fixed on the bolster side. A shearing section that can shear the material is provided by moving it so that the upper chamber of the drive cylinder device communicates with the upper chamber of the driven cylinder device so that the working fluid can reciprocate and is driven from the upper chamber of the drive cylinder device. With the working fluid flowing in the upper chamber of the cylinder device, the working fluid in the lower chamber of the driven cylinder device can be discharged to the outside, and the working fluid returns from the upper chamber of the driven cylinder device to the upper chamber of the driving cylinder device. In this state, the working fluid can be supplied from the outside into the lower chamber of the driven cylinder device, and the drive pin of the drive cylinder device is connected to the bolster side while the slide is lowered. Characterized in that it is rapidly lowered movable around a movable blade is brought into contact with the follower pin of the driven cylinder device with the position restraint possible and sliding downward after the position constrained by contact, a press machine.

  According to a second aspect of the present invention, the driven cylinder device includes a cylinder configured using the inner cylinder and a piston having a disk-shaped pressure receiving surface, and the drive cylinder device surrounds the inner cylinder and the cylinder. It is a double cylinder structure formed including a cylinder configured using an outer cylindrical body and a piston having an annular pressure receiving surface.

  According to a third aspect of the present invention, the outer cylindrical body and the inner cylindrical body are concentrically arranged, and the fourth aspect of the invention is a plurality of drive cylinder device drive pins arranged on a concentric circle locus. Furthermore, the invention of claim 5 is characterized in that a free running distance is provided between the driven pin and the movable blade.

  Further, in the invention of claim 6, the upper chamber of the drive cylinder device and the upper chamber of the driven cylinder device are formed so that the working fluid can reciprocate through a flow path formed in each cylinder.

  Furthermore, the invention of claim 7 is a die set structure in which the drive cylinder device and the driven cylinder device are attached to the upper plate detachably attached to the slide, and the shearing portion is attached to the lower plate detachably attached to the bolster. Yes.

  According to the first aspect of the present invention, high-speed and high-quality shearing can be performed by using the downward movement of the slide and increasing the slide speed. Since the complicated power transmission mechanism can be eliminated, it is possible to greatly reduce the cost and downsize the apparatus. In addition, since it is possible to produce sheared products as well as blanks, it is possible to increase productivity throughout the entire operation and improve the operating rate of the press machine itself.

  According to the invention of the second aspect, in addition to the effect of the invention of the first aspect, the apparatus cost can be further reduced and the size can be further reduced while further improving the rigidity of the both cylinder apparatuses.

  According to the invention of claim 3, in addition to the effect of the invention of claim 2, simplification of the structure of the cylinder device can be further promoted.

  According to the invention of claim 4, in addition to the effects of the inventions of claims 2 and 3, mechanical homogenization and stabilization regarding high-speed shearing can be achieved.

  According to the invention of claim 5, in addition to the effects of the inventions of claims 1 to 4, the descending speed of the driven pin can be accelerated in a no-load state, so that sharper shearing can be performed at a higher speed.

  According to the invention of claim 6, in addition to the effects of the inventions of claims 1 to 5, the piping between the cylinder devices can be wiped out, so that the structural safety is enhanced, the structure is simplified, the device cost is reduced, and the device Miniaturization can be further promoted.

  According to the invention of claim 7, in addition to the effects of the inventions of claims 1 to 6, the applicability to the shearing mode and object is wide. For example, the production of blanks and the production of sheared products can be switched quickly and accurately, and in this respect also productivity and availability can be improved.

  Hereinafter, the best mode for carrying out the present invention will be described in detail with reference to the drawings.

(First embodiment)
As shown in FIGS. 1 to 3, the present press machine has a drive cylinder device 20 having a large pressure receiving area Ak and a driven cylinder device 40 having a small pressure receiving area Aj mounted on the slide side (10) so as to be able to move up and down synchronously with the slide. The shearing portion 1 (fixed blade 2 and movable blade 5) is provided on the side (50), and the driven fluid is driven in a state where the working fluid is flowing from the upper chamber 23 of the drive cylinder device 20 to the upper chamber 43 of the driven cylinder device 40. The working fluid in the lower chamber (46) of the cylinder device can be discharged to the outside (63), and the working fluid is returned to the outer chamber (63) from the upper chamber 43 of the driven cylinder device to the upper chamber 23 of the driving cylinder device. ) In the lower chamber (46) of the driven cylinder device so that the working fluid can be supplied, and the drive pin 26 of the drive cylinder device abuts against the bolster side (counter pin 51) while the slide is lowered. Since that is rapidly lowered movable around a movable knife 5 with the follower pins 45.

  The right half centering on the base line Z in FIG. 1 (longitudinal sectional view) shows the state before executing the shearing process, and the left half shows the state after executing the shearing process. FIG. 2 is a plan view.

  The press machine moves the slide up and down by a drive mechanism (crank mechanism or servo motor drive mechanism), and presses the blank by cooperating with the upper die attached to the slide side and the lower die attached to the bolster side. Can be applied. However, since the structure of the press machine is well known, the illustration is omitted.

  In FIG. 1, the upper plate 10 has a structure that is detachable from the slide, and forms a slide side with respect to the shearing portion 1 and the cylinder devices (20, 40). That is, the drive cylinder device 20 (specifically, the cylinder 22) and the driven cylinder device 40 (specifically, the cylinder 42) can be moved up and down in synchronization with the vertical movement of the slide. The lower plate 50 is detachable from the bolster and forms the bolster side.

  In this embodiment, the die set structure is such that the drive cylinder device 20 and the driven cylinder device 40 are attached to the upper plate 10 detachably attached to the slide and the shearing portion 1 is attached to the lower plate 50 detachably attached to the bolster.

  Further, the drive cylinder device 20 and the driven cylinder device 40 have a cylindrical double cylinder structure. That is, the driven cylinder device 40 is configured using the inner cylinder 35, and the drive cylinder device 20 is configured using the inner cylinder 35 and the outer cylinder 31. The outer cylinder 31 and the inner cylinder 35 are concentrically arranged with the base line Z as the center (core).

  Specifically, the driven cylinder device 40 includes a cylinder 42 using the inner cylinder 35 and a driven piston 44 having a disk-shaped pressure receiving surface (pressure receiving area Aj), with the base line Z shown in FIGS. It is arranged. The cylinder 42 is formed of an inner cylinder 35, an upper lid portion (upper plate 10), and a lower lid portion 47. The upper side of the driven piston 44 is the upper chamber 43, and the lower side is the lower chamber 46. The driven piston 44 is integrally formed with a driven pin (equivalent to a piston rod) 45 extending downward.

  A communication hole 36 having a groove structure is formed in the inner cylindrical body 35 constituting the cylinder 42, and a communication hole 11 having a groove structure is also formed in the upper lid portion (upper plate 10). The communication holes 36 and 11 communicate the upper chamber 43 and the drive cylinder device 20 (upper chamber 23). Further, the lower lid portion 47 is provided with a communication path (communication pipe) 49, and the release port becomes the supply / discharge port 48.

  The drive cylinder device 20 includes a cylinder 22 configured using an inner cylinder 35 and an outer cylinder 31 surrounding the inner cylinder 35, and a drive piston 24 having an annular pressure receiving surface (pressure receiving area Ak). It is arranged around the base line Z. The cylinder 22 includes inner and outer cylindrical bodies 35 and 31, an upper lid portion (upper plate 10), and a lower lid portion 28. The upper side of the drive piston 24 is the upper chamber 23, and the lower side is the lower chamber 27. A driving pin (equivalent to a piston rod) 26 extending downward is integrally formed with the driving piston 24. As shown in FIG. 2, the number of drive pins 26 is a plurality (6) of pins arranged at equal intervals on a circular locus (R) centered on the base line Z.

  A communication passage 33 having a pressure adjusting port 32 is formed in the outer cylindrical body 31 constituting the cylinder 22, and the upper chamber 23 and the driven cylinder device 40 (upper chamber 43) communicate with the upper lid portion (upper plate 10). A communication hole 11 having a groove structure is formed.

That is, the working fluid passes through the flow path (33, 36, 11) in which the upper chamber 23 of the drive cylinder device 20 and the upper chamber 43 of the driven cylinder device 40 are processed into the cylinders (31, 10, 35, 10). It is formed so that it can reciprocate. Compared to the case of the external connection pipeline, the structure is simple and the safety against high pressure (for example, 200 kg / cm ² ) can be enhanced.

  Note that the lower lid portion 28 is provided with a through hole through which the drive pin 26 can be put in and out. Since the lower chamber 27 is open to the atmosphere (the lower chamber pressure 27P is atmospheric pressure), it is not necessary to provide a communication path or the like. That is, the lower lid portion 28 functions as a member that regulates the lower limit position of the drive piston 24.

  That is, the working fluid is communicated between the drive cylinder device 20 (upper chamber 23) and the driven cylinder device 40 (upper chamber 43) so as to reciprocate. The working fluid in the lower chamber (46) of the driven cylinder device is externally (tanked) while the working fluid is flowing from the driving cylinder device 20 (upper chamber 23) to the driven cylinder device 40 (upper chamber 43). 63) can be discharged.

  On the contrary, in a state where the working fluid is returning from the driven cylinder device 40 (upper chamber 43) to the drive cylinder device 20 (upper chamber 23), the lower chamber ( 46) can be supplied with working fluid.

  Here, the pressure receiving area Ak of the drive cylinder device 20 provided on the slide side (10) is large, and the pressure receiving area Aj of the driven cylinder device 40 is small. In this embodiment, the pressure receiving area Ak is five times (= Ak / Aj) the pressure receiving area Aj. That is, the amount Q23 of working fluid (for example, incompressible oil) flowing out from the drive cylinder device 20 (upper chamber 23) and the working fluid flowing into the driven cylinder device 40 (upper chamber 43) within a unit time. If the amount Q43 is equal, the displacement amount S44 of the driven piston 44 (driven pin 45) can be made five times the displacement amount S24 of the drive piston 24 due to the difference in pressure receiving area. That is, the descending speed of the driven pin 45 can be increased to five times the speed of the driving pin 26 (specifically, the descending speed of the slide).

  The slide motion (the diagram showing the relationship between the crank angle and the slide position) has a low speed area where the slide speed is desired as the press working area and a high speed to shorten the time immediately before the press working area. And an average speed region that is an average slide speed through a slide stroke (one up and down). For example, the slide speed in the high speed region is four times the average slide speed.

  Thus, if the above-described inflow and outflow of the working fluid is executed using the sliding speed (four times speed) in the high speed region, the descending speed of the driven pin 45 is 20 as compared with the average sliding speed. (= 5 × 4) times. Actually, since the descending speed of the slide itself is also added, it is close to 21 times.

  Now, the shearing section 1 attached to the bolster side (lower plate 50) moves the moving blade 5 shown in FIG. 1 and the fixed blade 2 disposed in the back of the paper relative to each other (moving up and down), A single material (material 9) can be created and produced by shearing the continuous material (material 9) inserted into the through holes 6 of the blades 2 and 5.

  The fixed blade 2 is fixed to an upper end block 55 and a lower end block 57, and the movable blade 5 is slidably mounted on a vertically extending guide 56 attached between the blocks 55 and 57. This is a so-called die set structure. A lifting piston 53 is fitted in a through hole 52 provided in the lower plate 50 (and the lower end block 57).

  The lifting piston 53 is connected to a lower cushion device (not shown). In a normal state (no load state), the movable blade 2 is raised to the upper limit position shown in the right half of FIG. Transmits the cushioning action, and at the end of the shearing process, the movable blade 2 can be lowered to the lower limit position shown in the left half of FIG.

  The lower plate (bolster side) 50 is provided with a counter pin 51 that substantially constitutes a part of the lower plate (bolster side). This number is the same as the number (six) of drive pins 26 on the slide side (10). The lengths of the drive pin 26 and the counter pin 51 are determined as values that allow both the pins 26 and 51 to come into contact with each other earlier than the time when the driven pin 45 comes into contact with the movable blade 5 when the slide (10) is lowered. The

  That is, the position of the drive pin 26 of the drive cylinder device 20 can be restricted by contact with the bolster (50) while the slide (10) is lowered. As the slide is lowered after the position is restricted, the driven pin 45 of the driven cylinder device 40 is brought into contact with the movable blade 5 so that the movable blade 5 can be rapidly lowered.

  In addition, in this embodiment, the idle running distance d shown in FIG. 1 is provided between the driven pin 45 and the movable blade 5, and the contact start time between the driven pin 45 and the movable blade 5 is determined as the drive pin 26 and the bolster. It is formed so as to be able to be delayed from the point of start of contact with the side (51). That is, the acceleration performance immediately before the follower pin 45 abuts can be promoted. Thus, the impact (shearing force) at the moment when the driven pin 45 contacts the movable blade 5 (material 9) can be strengthened.

  The supply / discharge device 60 includes a pump 61, a tank 63, a solenoid valve 65, a pilot check valve 74, a pressure adjustment valve 78, a pipe joint 79, and a flow path (pipe) shown in FIG. The lower chamber 46 is formed so that a working fluid can be supplied and discharged. The accumulator 72 is provided to keep the value of the upper chamber pressure 43P of the driven cylinder device 40 constant. Note that the value of the upper chamber pressure 23P of the drive cylinder device 20 is larger than the value of the upper chamber pressure 43P by an amount corresponding to the flow path resistance.

  When the solenoid valve 65 is switched to the lowering port 66 during the slide lowering, the working fluid in the driven cylinder device 40 (lower chamber 46) is supplied to the supply / discharge port 48, the pipe joint 79, the lower chamber pressure adjusting system (flow path). ) 75 and can be discharged to the outside (tank 63) through the pilot check valve 74 and the discharge pipe 64.

At the same time, the upper chamber pressure adjusting means [accumulator 72, upper chamber pressure adjusting system (flow path 73), pipe joint 79, and pressure adjusting port 32 are included. ], The working fluid urged (pressurized) by the pump 61 can be replenished through the pilot check valve 74, the flow path 76, and the pressure regulating valve 78. Therefore, the pressure in each upper chamber 42 and 23 during shearing can always be adjusted to a predetermined value (for example, 200 kg / cm ² ).

  It is possible to automatically switch from the descending port 66 to the neutral port 67 by detecting the moment when the drive pin 26 contacts the opposing pin 51. Switching to the other ports 66 and 68 is automatically performed by detecting the slide position (or moving direction).

  When switched to the neutral port 67, the two output ports of the solenoid valve 65 are both connected to return ports that return to the tank 63. That is, the two output ports of the solenoid valve 65 are at atmospheric pressure. As a result, there is no pressure at the two pilot portions of the pilot check valve 74. That is, the pilot check valve 74 remains closed, and both the lower chamber pressure adjustment system (flow path) 75 and the upper chamber pressure adjustment system 71 (flow path 76) are closed.

  When the slide port is switched to the rising port 68, the working fluid in the tank urged by the pump 61 is supplied to the supply pipe 62, the pilot check valve 74, the lower chamber pressure adjusting system (flow path) 75, It can be supplied into the driven cylinder device 40 (lower chamber 46) through the exhaust port 48. Further, the working fluid can be discharged from the upper chamber pressure adjusting system 71 to the tank 63 through the pressure adjusting valve 78 and the pipe 64.

  Next, the operation and operation of this embodiment will be described.

  Referring to the right half of FIG. 1, when the crank angle starts from 0 degree and the slide (upper plate 10) starts to descend from the top dead center, the cylinder devices 20, 40 descend synchronously. The drive pin 26 is pushed down by the upper chamber pressure 23P and is restricted in position (suspended) by the cylinder 22 (27).

  At this stage, the drive pin 26 has not yet contacted the opposing pin 51. The driven pin 45 is also not in contact with the movable blade 5. The upper chamber pressure 43P and the lower chamber pressure 46P of the driven cylinder device 40 are balanced.

  When the crank angle enters, for example, 90 degrees (high speed region), the lower end of the drive pin 26 comes into contact with the upper end of the opposing pin 51. When the drive cylinder device 20 (cylinder 22) is further lowered as the slide descends thereafter, the drive piston 24 is relatively moved in the direction of reducing the volume of the upper chamber 23 in FIG. The pressure 23P of the working fluid in the upper chamber 23 increases.

  Then, since the solenoid valve 65 is switched from the neutral port 67 to the descending port 66, the working fluid in the lower chamber 46 of the driven cylinder device 40 is discharged to the tank 63. The pressure 46P of the working fluid in the lower chamber 46 decreases. That is, the working fluid moves forward from the drive cylinder device 20 (upper chamber 23) to the driven cylinder device 40 (upper chamber 43) through the communication path (11 etc.).

  The descending speed of the driven piston 44 (driven pin 45) having the small pressure receiving area Aj is increased to 20 times the relative speed of the driving piston 24 and the cylinder 22 having the large pressure receiving area Ak. The descending speed of the slide (upper plate 1) itself is also weighted. That is, the driven pin 45 can be rapidly lowered at a significantly high speed (ultra-high speed) compared to the average slide speed. In addition, since the idling distance d is provided, acceleration can be promoted.

Thereafter, the lower end of the driven pin 45 comes into contact with the movable blade 5 and starts to shear the material 9 in cooperation with the fixed blade 2. The moving blade 5 moves downward at high speed. Since the pressure 43P (23P) in the upper chamber 43 (23) of the driven cylinder device 40 (and the drive cylinder device 20) is maintained at a predetermined value (for example, 200 kg / cm ² ) by the operation of the accumulator 72, the pressure is stable. High speed shearing is possible. The shear surface is of high quality.

  When the slide (10) starts to rise from the bottom dead center toward the top dead center, the solenoid valve 65 is switched to the lift port 68. Since the working fluid is supplied to the lower chamber 46 of the driven cylinder device 40 from the outside (63), the pressure in the lower chamber 46P is increased and the driven pin 45 (driven piston 44) is pushed up in the direction of reducing the internal volume of the upper chamber 43. . At this time, the working fluid in the upper chamber 43 is discharged to the tank 63 through the pressure adjustment valve 78. The upper chamber pressure 43P is not excessively increased.

  When the drive pin 26 moves away from the opposing pin 51 as the slide (upper plate 1) rises, the drive pin 26 (drive piston 24) is moved as shown in FIG. 1 by the pressure 23P in the upper chamber (23) of the drive cylinder device 20. The initial state shown in the right half of is restored. The solenoid valve 65 is temporarily switched to the neutral port 67.

  In this embodiment, the drive cylinder device 20 having a large pressure receiving area Ak and the driven cylinder device 40 having a small pressure receiving area Aj are attached to the slide side (10) so as to be able to move up and down synchronously and the upper chambers (23, 43) are connected to each other. The shearing portion 1 (fixed blade 2, moving blade 5) is provided on the bolster side (50), and the driven pin 45 is moved after the drive pin 26 is constrained by contact with the bolster side (51). Since the movable blade 5 is formed so as to be brought into rapid contact with the movable blade 5 so that it can be lowered rapidly, high-quality shearing can be performed at high speed by using the downward movement of the slide and increasing the slide speed. Therefore, it is possible to greatly reduce the cost and size of the apparatus. In addition, since it is possible to produce sheared products as well as blanks, it is possible to increase productivity throughout the entire operation and improve the operating rate of the press machine itself.

  In particular, after pressing (or before applying) a single piece of material (blank) created by shearing, give special post-processing (for example, polishing) to the end face (shearing surface) of the blank. It can respond to the request to make a product as it is.

  Also, as a consequential point in recent years [Because conventional shear processing equipment (or before and after the proposal) is a dedicated machine, after processing a large number of single-piece materials from continuous materials, it must be stopped. Absent. The higher the shearing speed, the longer the rest period. Occupancy rate is extremely low. On the contrary, from the press machine side, it is in a dormant state if no blank is supplied. If so, the press machine should be sheared to create a blank. In other words, from the viewpoint of further improving the accuracy and quality of blanks and parts of products (shear surfaces) and significantly reducing product costs, conventional shear processing equipment with low operating rate (or before and after the proposal) It is more than enough to meet the demand that it is difficult to allow the installation of

  Further, since the driven cylinder device 40 (inner cylinder 35) and the drive cylinder device 20 (inner cylinder 35, outer cylinder 31) have a double cylinder structure, the speed increasing conversion device is improved while increasing the rigidity of both cylinder devices. (20, 40) and cost reduction and downsizing of the press machine as a whole can be further promoted.

  Further, since the outer cylinder 31 and the inner cylinder 35 are disposed concentrically, the structure of the cylinder device can be simplified.

  Since there are a plurality (6) of drive pins 26 of the drive cylinder device 20 arranged on the concentric circle locus (R), mechanical homogenization and stabilization regarding high-speed shearing can be achieved.

  Since the idle running distance d is provided between the driven pin 45 and the movable blade 5, the descending speed of the driven pin 45 can be accelerated in a no-load state. Therefore, the shearing process can be performed at a higher speed and sharper.

  Further, the upper chamber 23 of the drive cylinder device 20 and the upper chamber 43 of the driven cylinder device 40 reciprocate the working fluid through the flow paths (33, 36, 11) processed in the cylinders (31, 35, 10). Therefore, the piping between the cylinder devices can be wiped out. In other words, structural safety can be enhanced and further simplification of the structure, reduction of the apparatus cost, and reduction of the apparatus size can be promoted.

  Since the drive cylinder device 20 and the driven cylinder device 40 are attached to the upper plate 10 detachably attached to the slide and the shearing portion 1 is attached to the lower plate 50 detachably attached to the bolster, Wide adaptability to the subject. For example, the production of blanks and the production of sheared products can be switched quickly and accurately, and the productivity and operating rate can be further improved.

(Second Embodiment)
In this embodiment, as shown in FIG. 4, the plate member 88 is formed so as to be capable of high-speed shearing. Since the drive cylinder device 20 and the driven cylinder device 40 are the same in structure and function as those in the first embodiment (FIGS. 1 to 3), description thereof will be omitted.

  In FIG. 4, a lower mold 86 that constitutes a plate shearing mold 80 together with an upper mold (84) is attached to the lower plate 50 via an end block 87 having a through hole. The upper die (punch 84) is attached to the punch holder 81 downward. The punch holder 81 is held by a plate presser 83 via a spring 82. The plate presser 83 is supported on the lower plate 50 via a support spring (not shown) stronger than the spring 82.

  In the state shown in the right half of FIG. 4 (no load state), the tip (lower end) of the punch 84 is within the through hole of the plate retainer 83. The driven pin 45 descends and pushes down the punch holder 81 against the upward biasing force of the spring 82. When the spring 82 starts to contract and the contraction proceeds until the upward biasing force of the supporting spring is overcome, the plate presser 83 presses the plate member 88 against the lower mold 86.

  When the driven pin 45 is further lowered, the punch 84 shears the plate material 88 to produce a material (blank or product) 89. The material 89 is discharged downward through the end block 87 and the through hole 52 of the lower plate 50.

  Therefore, also in this embodiment, high-speed shearing can be performed stably and reliably as in the case of the first embodiment. If this plate material shearing die (shearing part) 80 is replaced with the shearing part 1 shown in FIG. 1, a continuous material (6) is sheared at high speed to quickly and reliably produce a plurality of single-piece materials (blanks). Can be created.

  In the first and second embodiments described above, the double cylinder structure is formed by combining one drive cylinder device 20 and one driven cylinder device 40. However, the present invention is not limited to this structure. For example, the present invention can be implemented even if it is constructed as a combination structure of an arbitrary number of drive cylinder devices (20) and driven cylinder devices (40) each having one or two or more independent structures.

  The present invention can perform high-speed shearing suitable for producing a blank having a high-quality shear surface and producing a sheared product efficiently.

It is a longitudinal cross-sectional view for demonstrating the 1st Embodiment of this invention. Similarly, it is the top view which carried out the cross section of a part. Similarly, it is a system diagram for explaining a supply and discharge device. It is a longitudinal cross-sectional view for demonstrating the 2nd Embodiment of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Shear processing part 2 Fixed blade 5 Moving blade 10 Upper plate (slide side)
20 Drive cylinder device 31 Outer cylinder body 35 Inner cylinder body 40 Drive cylinder device 50 Lower plate (bolster side)
60 Feeder / Ejector 80 Sheet metal shearing mold

Claims (7)

A drive cylinder device with a large pressure receiving area and a driven cylinder device with a small pressure receiving area are mounted on the slide side so as to be able to move up and down synchronously with the slide.
A shearing section is provided that can shear the material by moving the moving blade relative to the fixed blade fixed on the bolster side.
With the upper chamber of the drive cylinder device and the upper chamber of the driven cylinder device communicating with each other so as to reciprocate, the working fluid is flowing from the upper chamber of the drive cylinder device to the upper chamber of the driven cylinder device. The working fluid in the lower chamber of the driven cylinder device can be discharged to the outside, and the working fluid is returning from the upper chamber of the driven cylinder device to the upper chamber of the driving cylinder device to the lower chamber of the driven cylinder device from the outside. Can be supplied to form,
The drive pin of the drive cylinder device can be restrained by contact with the bolster side while the slide is lowered, and the movable blade can be lowered rapidly by bringing the driven pin of the driven cylinder device into contact with the slide descending after the position restraint. A press machine that is capable of high-speed shearing.   The driven cylinder device includes a cylinder configured using an inner cylinder and a piston having a disk-shaped pressure receiving surface, and the drive cylinder device uses the inner cylinder and an outer cylinder surrounding the cylinder. 2. A press machine capable of high-speed shearing according to claim 1, wherein the press machine has a double cylinder structure including a cylinder configured as described above and a piston having an annular pressure receiving surface.   The press machine capable of high-speed shearing according to claim 2, wherein the outer cylinder body and the inner cylinder body are arranged concentrically.   The press machine capable of high-speed shearing according to claim 2 or 3, wherein a plurality of drive pins of the drive cylinder device are arranged on a concentric circle locus.   An idle running distance is provided between the driven pin and the movable blade, and the contact start time between the driven pin and the movable blade is formed so as to be delayed from the contact start time between the drive pin and the bolster side. A press machine capable of high-speed shearing according to any one of claims 1 to 4.   The upper chamber of the driving cylinder device and the upper chamber of the driven cylinder device are formed so that the working fluid can reciprocate through flow paths formed in the cylinders. Press machine capable of high-speed shearing.   7. The die set structure according to claim 1, wherein the drive cylinder device and the driven cylinder device are attached to an upper plate detachably attached to the slide, and the shearing portion is attached to a lower plate detachably attached to the bolster. A press machine capable of high-speed shearing described in any one of the above.

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