JP2007090419A - Press provided with shearing device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a press which is provided with a shearing device of a small size and by which high-speed machining is possible. <P>SOLUTION: The shearing device has: a shearing part including a fixed blade and a movable blade; a speed increasing linkage which includes a link lever having a driver element near by a supporting pin and a follower element far from the pin and is rotatable around the supporting pin and by which speed increasing function is revealable; an primary pressurizing block for transmitting original pressurizing force with the descending motion of a slide to a link lever; and a secondary pressurizing block for transmitting downward secondary pressurizing force with the rotational motion of the link lever to the movable blade; wherein the descending speed of the secondary follower element is increased to a speed faster than the descending speed of the slide by linked motion of the speed increasing linkage in synchronism with the descending motion of the slide. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a press machine provided with a shearing device for forming a single-piece material for press processing by shearing a continuous material.

  In a press machine that performs selected press processing (for example, drawing, forging, punching) on a single material (blank) that is carried in (supplied) from the outside, a blank supply device or a shearing device is attached to the front. The blank supply device can accommodate a plurality of single-piece materials and can feed them one by one. The shearing device shears a fed continuous material (bar material, strip-shaped plate material, etc.) to form a single material for pressing. The formed single-piece material is carried into the first stage (die) of the press machine using blank carrying-in means.

  Since the conventional shearing device has a structure in which the movable blade is moved relative to the fixed blade to perform the shearing process, the structure of the shearing part itself is compared with the structure of a simple container-like blank supply device. Complex and large. Also, a complicated power transmission mechanism (gear train, connecting rod, cam drive unit, cam) between a drive source (for example, main motor or main shaft) mounted in the crown of the press machine and the drive shaft for the movable blade Etc.).

  Also, since the drive power of the shearing machine is taken from the drive source (main shaft rotational power) of the press machine, the drive speed of the press machine (rotary speed of the main shaft) is compared with the normal drive speed (during press work operation). Thus, when the speed is switched to a low speed (for example, during a trial driving operation), the shearing speed becomes slow. That is, there is a problem that the quality / accuracy (perpendicularity, burr, roughness, etc.) of the sheared surface of the single material is lowered.

With regard to this point, a forging forming apparatus whose primary meaning is to prevent a reduction in shearing speed has been proposed (see, for example, Patent Document 1). This proposed apparatus is provided with a sub-drive mechanism for a movable blade including a sub-drive source, and the sub-drive mechanism is constructed so that the sub-drive mechanism can operate in preference to the main drive mechanism for a movable blade including a main drive source. The operating structure. When used as a blank supply means, the forging forming device is installed in front of the press machine as in the case of the conventional shearing device.
JP 2003-220443 A

  By the way, this proposed apparatus can achieve an extremely high shearing speed compared with the conventional shearing apparatus described above, if attention is paid to the finishing accuracy of a single-piece material. It seems to be applicable to exceptional and exceptional cases that require materials. However, it is pointed out that from the viewpoint of actual operation (expansion and expansion), it is difficult to meet the demands for universal downsizing and cost reduction, and the equipment cost is high, so that it is not acceptable for press machines. In addition, there is a troublesome handling due to timing setting for priority operation and introduction of an interlock. There is also a problem of shortening the maintenance work.

  However, the absolute value of the shearing speed cannot be increased beyond the shearing speed corresponding to the press drive speed (rotation speed of the main shaft) with the conventional shearing machine described above. That is, there is a case where deterioration of the quality of a single material is unavoidable. Moreover, it becomes impossible to meet the demand for further downsizing of the press machine.

  An object of the present invention is to provide a press machine provided with a shearing apparatus that can achieve downsizing of the apparatus while increasing the shearing speed.

  According to the proposed apparatus described above, the drive (rotation) speed of the drive source is switched to a lower speed [rpm1 = rpm10 × (1/10)] than the normal drive speed (rpm10) corresponding to the press speed (for example, spm10). Even in the case where the shearing speed is set, the value of the shearing speed is not the low speed (Srpm1) corresponding to the driving speed (rpm1) but the normal shearing corresponding to the normal driving speed (rpm10) by using the auxiliary driving source and the auxiliary power transmission mechanism. It can be preferentially and forcibly switched to the same value as the processing speed value (Srpm10).

  In other words, in the above-described conventional shearing apparatus, the shearing speed of the main driving source is low without the auxiliary driving source and the auxiliary power transmission mechanism, that is, the main driving source is used and the main driving source is at a low speed (rpm 1). If the absolute value can be greater than or equal to the absolute value (Srpm10) of the normal shearing speed corresponding to the normal driving speed (rpm10), the conventional problem (decrease in shearing speed at low speed) can be solved. It should be possible to promote downsizing of the apparatus while wiping.

  In the present invention, (1) in the press machine, even if the drive speed of the main drive source is constant at a value (rpm) corresponding to the set press speed (spm), the slide lowering speed (Vspm) is not constant. In other words, for example, a low speed (Vspml) region near the bottom dead center, a high speed (Vspmh) region near the bottom dead center, and an average speed corresponding to the driving speed (spm), such as the slide motion shown in FIG. It must be established from a combination of areas (Vspmm). (2) As long as the material of the continuous material is general, there is a practical upper limit for the absolute value of the shearing speed, and it is not necessary to increase the speed excessively. (3) If it can be constructed so that it can be driven using a slide, the power transmission mechanism can be compared with the conventional power transmission mechanism (eg, gear train, connecting rod, cam drive unit, cam, etc.). The structure can be greatly simplified and reduced in size, and as a result, it is effective for simplifying and reducing the size of the entire press machine. In addition, compared with the case of the proposed device, complete synchronous operation is possible without providing an electrical interlock. Be sure to do it. It was created by paying attention to technical matters unique to press machines.

  That is, the present invention is characterized in that the power transmission mechanism of the shearing apparatus is formed of a speed increasing link mechanism that is synchronized with the vertical movement of the slide and that can express a speed increasing function.

  That is, the press machine provided with the shearing device according to the invention of claim 1 is a press machine provided with a shearing device for forming a single material for press processing from a continuous material by shearing, A device including a fixed blade fixed to the main body block and a movable blade mounted so as to be movable up and down with respect to the fixed blade; A speed increasing link mechanism that includes a link lever having a driving node element closer to the support pin mounted on the block and a follower node element far from the support pin, and that can rotate around the support pin as a whole and express a speed increasing function. And an original pressure block attached to the slide so as to be able to transmit the applied pressure accompanying the downward movement of the slide to the link lever while being engaged with the driving node element, and the driven node element While having a secondary pressure block that can transmit the downward secondary pressure accompanying the pivoting movement of the link lever to the movable blade, slide in the shearing region where the primary pressure block and the prime node element are engaged. The descending speed of the follower element can be increased to a speed faster than the slide descending speed by the interlocking movement of the speed increasing link mechanism synchronized with the descending movement, and added to the movable blade from the follower element that descends at a high speed after the acceleration. It is formed so that it can be sheared using the applied applied pressure.

  In the invention of claim 2, the range of the shearing region can be set and changed by adjusting the position of the driving node element in the horizontal direction. In the invention of claim 3, the shearing start position can be set and changed by adjusting the position of the driving node element in the vertical direction.

  Further, the invention of claim 4 has a structure in which a plurality of speed increasing link mechanisms are combined, and in the invention of claim 5, the driving node pin forming the driving node element and the original pressure block are formed so as to be capable of surface engagement. ing. In the invention of claim 6, the main body block is formed from a die set or the like constituting a part of the press machine.

  According to the first aspect of the present invention, it is possible to simultaneously increase the shearing speed and reduce the size of the apparatus, stably and surely perform the shearing operation completely synchronized with the pressing operation, and reduce the press driving speed ( In spite of switching to (rpm), it is possible to ensure the high quality of the single material. The cost of the press machine as a whole can be reduced.

  Moreover, according to the invention of Claim 2, the adaptability to the dimensional change in the shearing direction of the continuous material can be further expanded as compared with the case of the invention of Claim 1. Further, according to the invention of claim 3, as compared with the cases of the inventions of claims 1 and 2, the adaptability of the continuous material to the vertical set position change can be further expanded.

  Furthermore, according to the invention of claim 4, compared with the case of each invention of claims 1 to 3, the shearing speed corresponding to the selected slide lowering speed while avoiding high rigidity and large size. And the vertical movement stroke of the movable blade can be shortened. According to the invention of claim 5, as compared with the cases of the inventions of claims 1 to 4, a stable engagement state between the original pressure block and the prime mover element can be secured and the prime mover element Can reduce deformation and wear. Further, according to the invention of claim 6, compared to the case of each invention of claims 1 to 5, for example, it is easy to switch to a shearing speed optimum for a set mold or continuous material. is there.

  The best mode for carrying out the present invention will be described below with reference to the drawings.

(First embodiment)
As shown in FIGS. 1 to 3, the present press machine 10 has a structure including a shearing device 30 capable of forming a single material 91 for pressing from a continuous material 90 by shearing. The shearing device 30 includes a shearing unit 31, a speed increasing link mechanism 51, an original pressure block 12, and a sub pressure block 61, and a speed increasing link mechanism that synchronizes with the downward movement of the slide 11 in the shearing region. By the interlocking movement 51, the descending speed of the follower pin 57 can be increased to a speed faster than the slide descending speed, and the follower pressure applied to the movable blade 35 from the follower pin 57 that moves downward at a high speed after the acceleration is increased. It is formed so that it can be sheared while being used.

  1 to 3, the press machine 10 is a slide shown in FIGS. 1 and 2 through a crank mechanism [crankshaft (eccentric portion), connecting rod, etc.] that is rotationally driven by a main motor (drive source) (not shown). 11 can be reciprocated in the vertical direction. A mold (upper mold) (not shown) is attached to the slide 11. The vertical reciprocation of the slide 11 follows the motion curve (crank angle θ−slide position P curve) shown in FIG.

  Paying attention to this motion curve, even if the rotational driving speed of the driving source is a constant value (rpm) corresponding to the set spm (the number of sliding strokes per minute), the sliding speed corresponds to the set spm. It is understood that not only the average speed (Vspmm) but also the high speed (Vspmh) and the low speed (Vspml) change depending on the crank angle θ (slide position P). Details of the relationship with the speed increasing link mechanism 51 will be described later.

  In FIG. 1, a die set 21 constituting a part of the press machine 10 is detachable from a known bed (or bolster) not shown. In some cases, a die plate is used. A lower die (die) is attached to the die set 21. In this embodiment, the die set 21 is also used as a main body block (21) constituting a part of the shearing device 30. That is, it is a means for facilitating the downsizing of the apparatus while facilitating the work for incorporating (equipping) the shearing apparatus 30 into the press machine 10 integrally. The die set 21 is provided with a movable blade moving space (hole) 23 extending in the vertical direction shown in FIGS. 1 and 2 and a block moving space (hole) 22 shown in FIG.

  Now, the shearing section 31 which is the main part of the shearing apparatus 30 is moved up and down with respect to the fixed blade 32 (32U, 32D) fixed to the main body block (die set 21) shown in FIG. The movable material 35 includes a movable blade 35 that can be mounted, and the continuous material 90 is sheared by the downward movement of the movable blade 35 and in cooperation with the stationary blade 32 on the stationary side to obtain a single material (blank) 91. it can.

  Although the structure and form of the double blades 32 and 35 are not particularly limited, the fixed blade 32 is a continuous material that has been fed in a predetermined direction (from right to left in FIG. 1) by feed means (not shown). The upper blade 32U and the lower blade 32D that are arranged to face each other with a gap that can penetrate through 90 can be stably held on the tip side of the continuous material 90. That is, the shearing process can be performed smoothly and reliably. The material and form of the continuous material 90 are not limited, but in this embodiment, it is a long metal round bar. It may be a strip-shaped plate material, a hollow rod-shaped material, or the like.

  In this embodiment, a die (lower die) and a fixed blade 32 corresponding thereto are attached to the main body block (die set 21) in advance. When the die set 21 is exchanged for the die exchange, the fixed blade 32 (32U, 32D) having a form corresponding to the form of the blank to be pressed (single piece material 91), that is, the continuous material 90 in the die is automatically set. Can be exchanged. The main body block may be formed with a die set plate or a stationary side member (main body frame or the like) of the press machine 10 instead of the die set 21.

  The forward end of the continuous material 90 fed from the right direction in FIG. 2 passes through (penetrates) the gap between the fixed blades 32U and 32D, and then comes into contact with the material position regulating member (stopper) 75. By restricting the position of the continuous material 90 in the horizontal direction, the length (dimension) of the single material (short-sized round bar) 91 can be kept constant. The fixed blades 32U and 32D may be formed so as to be close to each other before and after the position restriction of the continuous material 90. In this regard, the movable blades 35U and 35D may be similarly formed.

  However, in this embodiment, as in the case of the fixed blade 32, the movable blade 35 and the upper blade 35U disposed opposite to each other with a gap capable of penetrating the continuous material 90 fed from the fixed blade 32 side. The lower blade 35D is formed and mounted (held) on the movable blade fixed position holding means 80.

  This movable blade fixed position holding means 80 allows the downward movement of the movable blade 35 while maintaining an upward reaction force (biasing force) against the downward pressure from the driven node pin 57 side at least in the shearing region. After the single material 91 is carried into the first stage side of the press machine 10 and the link lever 52 returns to the initial (horizontal) state shown in FIG. 1, the movable blade 35D is moved to a fixed position (see FIG. 1). A function of returning to the position shown).

  Thus, the movable blade fixed position holding means 80 may be constructed using a spring mechanism, an elevating means or the like. In this embodiment, the cylinder device (cylinder 81, piston rod 82) shown in FIG. 1 is formed, and the lower end portion of the holder 63 is connected to the upper end portion of the piston rod 82.

  The speed increasing link mechanism 51 that is characteristic of the present invention constitutes a new power transmission mechanism that replaces the above-described conventional power transmission mechanism (for example, gear train, connecting rod, cam drive unit, cam, etc.). It includes a link lever 52 having a drive node element (drive node pin 55) closer to the support pin (support shaft) 53 attached to the (die set 21) and a follower element (drive node pin 57) farther away. As a whole, it is formed so as to be rotatable around the support pin 53 and to exhibit a speed increasing function.

  1 and 3, the link lever 52 is formed of a pair of link lever elements 52L and 52R. It is intended to further reduce the weight while ensuring sufficient rigidity of the entire link lever (52). A support pin hole 52S, a driving node pin hole 52G, and a driven node pin hole 52J are provided at corresponding positions of the link lever elements 52L and 52R, respectively.

  The support pin 53 is fitted in the left and right support pin holes 52S, and extends between the link levers 52L and 52R facing each other. This support pin (support shaft) 53 is provided across a pair of left and right bearing blocks 25L, 25R. Thus, the link lever 52 is rotatable about the support pin 53. Note that the collar 54 is interposed in order to make the interval between the link lever elements 52L and 52R constant.

  A driving node pin 55 is fitted between the both driving node pin holes 52G. The driving node pin 55 is integrally fixed to the link lever 52 (52L, 52R) by using an auxiliary plate 56P and an auxiliary block 56B provided at both lower ends of the link lever elements 52L, 52R. The auxiliary block 56B is fixed to the upper surface of the auxiliary plate 56P located between the inner wall surfaces of the link lever elements 52L and 52R. Therefore, even if a downward original pressure is applied, the driving node pin 55 is not greatly deformed downward, so that the original pressure can be efficiently transmitted to the driven node pin 57 side. It is also effective from the viewpoint of extending the service life.

  In other words, the link lever 52 is formed of a pair of link lever elements 52L and 52R disposed to face the support pin 53, and the drive node pin 55 extends (passes) between the link lever elements. Formed from. The upper side of the driving node pin 55 has a planar shape (upper end surface 55U) opposite to the lower end surface (plane) 12D of the original pressure block 12, and the lower side is provided between the link lever elements (52L, 52R). The auxiliary block 56B is integrally locked.

  A driven node pin 57 forming a driven node element is fitted between the driven node pin holes 52J, and a driven roller 58 is fitted between the link lever elements 52L and 52R of the driven node pin 57.

  Here, the center distance between the support pin 53 and the driving node pin 55 is Ls (for example, “1”), and the center distance between the support pin 53 and the driven node pin 57 is L1 (for example, “4”). For example, a speed-up function of 4 times “= (Ll / Ls)” can be expressed. Incidentally, on the motion curve shown in FIG. 9, for example, the crank angle (θ) range, that is, the slide position (P) range in which the value of the high speed (Vspmh) is four times the value of the average speed (Vspmm) is sheared. If the region is selected, the shearing speed (Sspm) is 16 (= 4 × 4) times the average speed (Vspmm).

  The original pressure block 12 is attached to the lower surface of the slide 11 and substantially forms a part of the slide 11, and the slide 11 moves downward while being engaged with the prime node element (primary node pin 55). It is possible to transmit the downward original pressurizing force accompanying to the link lever 52. Corresponding to the lower end surface (plane) 12D forming the engagement surface, the upper side of the drive node pin 55 is processed into a planar shape (upper end surface 55U). Thus, the original pressure from the slide 11 can be reliably transmitted to the link lever 52 via the both surfaces 12D and 55U that are closely engaged. Both surfaces 12D and 55U can be relatively displaced (moved) smoothly in the horizontal direction.

  As the slide 11 descends, the link lever 52 rotates clockwise about the support pin 53 (right rotation), so the upper end surface (plane) 55U is left in FIG. 1 with respect to the lower end surface (plane) 12D. It moves (displaces) in the direction. In this embodiment, since the right side of the upper end surface (plane) 55U in FIG. 1 is moved (separated) to the left side of the lower end surface (plane) 12D after the shearing of the single-piece material 91 is completed, the original processing of the slide 11 is performed. No pressure is applied to the link lever 52 and the slide 11 can move downward toward the bottom dead center. At this time, since the original pressure block 12 can move (pass) through the block moving space 22, the smooth downward movement of the slide 11 can be secured.

  Next, the sub pressure block 61 transmits the downward sub pressure applied to the movable blade 35 along with the rotational movement around the support pin 53 of the link lever 52 while engaging with the driven node element (driven node pin 57). Is possible. In this embodiment, the sub pressure block 61 is formed of a holder 63 and a head 62 that are slidably fitted to a sliding guide (not shown).

  The lower end surface (plane) 58D of the driven roller 58 is formed in a planar shape corresponding to the upper end surface (plane) 62U of the head 62. Therefore, the downward applied pressure from the link lever 52 (the driven node pin 57) can be reliably transmitted to the head 62 (holder 63) side through the both surfaces 58D and 62U that are closely engaged.

  Since the head 62 is biased upward by the upward reaction force (biasing force) of the movable blade fixed position holding means 80, if the driven roller 58 is rotatably fitted to the driven node pin 57, Even if the link lever 52 is inclined in the shearing region, it is possible to maintain the close contact state between the engagement surfaces 58D and 62U.

  Here, the shearing region means a state (range) in which the original pressure block 12 (12D) and the driving node element [the driving node pin 55 (55U)] are closely engaged. That is, as shown in FIG. 1, the state where the original pressure block 12 (12D) that has been lowered is engaged with the driving node pin 55 (55U) is the shearing start position by the movable blade 35, and the upper end surface 55U The state in which the right side is moved (separated) to the left side of the lower end surface 12D is the shearing end position.

  However, in this embodiment, the movable blade 35 (single product material 91) is moved from the position shown in FIG. 2 (from the shearing position) for convenience in handling in relation to the press machine (first stage) of the single product material 91. Are also lowered to a lower position.)

  In this sense, the shearing region is a wide area (region) expanded to a position below the position at the end of shearing processing, that is, a region expanded from the original shearing region. Incidentally, in FIG. 1, the engagement state of both (12D, 55U) can be released early by adjusting the position of the driving node pin 55 (55U) to the left with respect to the original pressure block 12 (12D). By doing so, the position at the end of the shearing process can be matched with the original position at the end of the shearing process.

  When passing through the shearing region, the drive node pin 55 slides on the left end surface 12S of the original pressure block 12, that is, the link lever 52 cannot rotate and the link lever 52 is in the inclined state shown in FIG. It does not prevent further lowering of the pressure block 12. When the original pressure block 12 moves upward from the position shown in FIG. 2 as the slide 11 moves upward toward the top dead center, the link lever 52 moves in the clockwise direction by the action of the return spring 71. It rotates in the opposite direction (left rotation) and returns to the initial state (horizontal state) shown in FIG. The initial state (appearance state) is maintained by the cooperation of the return spring 71 and the stopper 72.

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

  In FIG. 1, the lower end surface 12 </ b> D of the original pressure block 12 abuts (engages) with the upper end surface 55 </ b> U of the driving node pin 55 as the slide 11 moves downward. Shearing is started. That is, when the original pressure block 12 is lowered, the link lever 52 rotates clockwise around the support pin 53. Then, since the driven node pin 57 (driven roller 58) applies a downward applied pressure to the driven pressure block 61 (head 62), the movable blade 35 moves downward to shear the continuous material 90 in relation to the fixed blade 32. Process. The movable blade fixed position holding means 80 (80C) allows the movable blade 35 to move downward.

  When the original pressure block 12 (12D) moves relatively to the left and is disengaged from the drive node pin 55 (55U), the applied pressure is not applied to the link lever 52. Since the original pressurizing block 12 after the separation descends in the block moving space 22, the downward movement of the slide 11 is not hindered. At this stage, the driving node pin 55 is restrained by the left end surface 12S of the original pressure block 12. Even if the urging force of the return spring 71 is present, the link lever 52 is maintained in the inclined state shown in FIG.

  In FIG. 2, when the driven node pin 57 (driven roller 58) is separated from the driven pressure block 61 (head 62) and is disengaged, the applied pressure is not applied to the driven pressure block 61. Ends. A blank (short-sized round bar) 91 formed by shearing is carried into a first stage of the press machine 10 by a carrying-in means at a predetermined position. The first stage is provided on the depth side in a direction perpendicular to the paper surface in FIG.

  When the slide 11 finishes pressing and starts to move upward from the bottom dead center to the top dead center, the original pressure block 12 also rises in synchronization. When the slide 11 (lower end surface 12D) rises from the position shown in FIG. 2, the position restriction by the left end surface 12S of the driving node pin 55 is released, so that the link lever 52 moves the support pin 53 by the action of the return spring 71. It rotates counterclockwise to the center and is restrained by the stopper 72. That is, it returns to the initial state shown in FIG.

  Thereafter, the movable blade fixed position holding means 80 works to raise the movable blade 35 and return it to the fixed position (see FIG. 2). The head 62 (62U) contacts the driven roller 58 (58D). Subsequently, the continuous material 90 is pushed in until the leading end of the continuous material 90 contacts the material position regulating member 75. Thereafter, the slide 11 moves downward for the next process.

  Here, consider a case where the drive speed (rotational speed) of the drive source is a constant value (rpm 10) corresponding to the set press speed (for example, spm10), and the average slide speed at that time is Vspm10. In a conventional power transmission mechanism (for example, gear train, connecting rod, cam driving unit, cam, etc.), when the driving speed is rpm 10, the shearing speed is usually Sspm 10, and the quality of the single-piece material 91 is It is good.

  In Patent Document 1, since the conventional power transmission mechanism is premised, the drive speed (rotation speed) is changed to a low speed [rpm1 = rpm10 × (1/10)] as in the case of trial driving (spm is spm1). If it does, a shearing speed will fall to the low speed (Srpm1) of 1/10 of a normal shearing speed (Srpm10). That is, the quality of the single-piece material 91 after the shearing process is deteriorated. Thus, a sub-drive source and a sub-power transmission mechanism that are separate from the main drive source are provided, and a measure is taken to forcibly increase to Srpm10 or higher using the sub-drive source.

  However, according to the present invention, the power transmission mechanism is constructed not to be driven directly by a drive source but to be driven via a slide drive mechanism (motion curve), so that the drive speed (rotational speed) described above is low. Even in the case of the speed (rpm1), the operation can be performed with the shearing speed being equal to or higher than the normal shearing speed (Srpm10).

  This is because even when the average slide speed is Vspm1 corresponding to the driving speed (rpm1) as in the trial hit (spm1), for example, as shown in FIG. 9, for example, three times higher speed (Vspmh = Vspm × 3 ) Can be input to the link lever 52 (the driving node pin 55) and output to the driven node pin 57 through the speed increasing link mechanism 51 as, for example, a quadruple speed, resulting in 12 (= 3 × 4) times as a result. Can be sheared at a speed Sspm (= Vspm × 12).

  Thus, according to this embodiment, the interlocking movement of the speed increasing link mechanism 51 synchronized with the downward movement of the slide 11 in the shearing region in which the original pressure block 12 and the driving node pin 55 are engaged. Thus, the descending speed of the follower pin 57 can be increased to a speed faster than the slide descending speed, and can be sheared using the follower pressure applied from the follower pin 57 that moves downward at a high speed after the acceleration. As a result, it is possible to increase the shearing speed and reduce the size of the apparatus at the same time, and to perform the shearing operation in complete synchronization with the pressing operation stably and reliably. Moreover, the high quality of the single-piece material 91 can be ensured regardless of the switching of the driving speed (rpm) to a low speed. The cost of the press machine (10) as a whole can be reduced.

  Further, since the power transmission mechanism (acceleration link mechanism 51) can be integrally incorporated in the main body block (die set 21), a dedicated location for the shearing device is provided in front of the press machine 10 (before the paper surface in FIG. 2). Compared to the case of the conventional power transmission mechanism that required the device, the installation space for the device can be greatly reduced, and the troublesomeness in layout and handling can be reduced.

  On the other hand, when the driving speed (rpm) is constant, the single-piece material 91 with higher accuracy can be obtained by selectively setting a shearing speed 10 times or more, for example, as compared with the conventional example. It is possible.

  In addition, since the drive node element (drive node pin) and the original pressure block 12 are formed so as to be able to engage with each other, a stable engagement state between the original pressure block 12 and the drive node element (55) is ensured. And can reduce the deformation and wear of the driving node element.

  Furthermore, since the main body block 12 is formed from the die set 21 that constitutes a part of the press machine 10, for example, it is easy to switch to a shearing speed optimum for a new mold that has been replaced and set.

(Second Embodiment)
In this embodiment, as shown in FIG. 4, a plurality of (2) units of the speed increasing link mechanism 51 are followed by a follower node element (the link upper right end 57A) of the speed increasing link mechanism 51A. It is arranged in series between the primary pressure block 12 and the secondary pressure block 61 so as to be engageable with the primary node (primary node pin 55) of the speed increasing link mechanism 51B. It can be constructed using three or more speed increasing link mechanisms.

  If, for example, a speed increase of 12 times is obtained with one speed increasing link mechanism 51 as in the first embodiment, the link lever 52 (52L, 52R) becomes long. Then, since it is necessary to greatly increase the rigidity of the speed increasing link mechanism 51 as a whole, there are disadvantages of an increase in the size of the apparatus, high cost, and unstable operation. In addition, since the vertical movement stroke of the movable blade 35 is excessive (long), the main body block (die set 21) is increased in size, that is, the press machine 10 is increased in size. This second embodiment is beneficial to clear out such disadvantages.

  Compared to the case of the first embodiment (FIG. 1), the triple acceleration type pre-acceleration link mechanism 51A is provided with a driving node pin 55 below the left side of the support pin 53, and the driven node element is a link lever. It is formed from the upper right end 57A of 52L (52R). The follower node element may be formed of a pin member or a plate member provided between the link levers 52L and 52R. Since the link lever 52 rotates counterclockwise around the support pin 53 as the slide 11 (original pressure block 12) descends, the driven node element 57A rises.

  The post-acceleration link mechanism 51B is provided with a driving node pin 55 on the upper left side of the support pin 53 as compared with the case of the first embodiment (FIG. 1). The driven node element (driven node pin 57) is provided on the right side of the link bar element 52B as in the case of FIG. A quadruple speed increase type. As the link lever 52 rotates clockwise around the support pin 53 as the slide 11 (original pressure block 12) descends, the driven node pin 57 (driven roller 58) descends. Thereby, the shearing speed can be increased to 12 times the average slide speed.

  The vertical movement stroke of the movable blade 35 is determined by the vertical movement stroke of the driven node pin 57 of the rear acceleration link mechanism 51B, and the vertical movement stroke of the driven node element 57A of the front acceleration link mechanism 51A is not weighted. That is, an increase in the vertical movement stroke of the movable blade 35 can be prevented.

  Thus, according to this embodiment, the same effect as in the case of the first embodiment can be obtained, and the shearing speed corresponding to the selected driving speed while avoiding high rigidity and large size. The vertical movement stroke of the movable blade 35 with respect to the speed increase rate can be shortened.

(Third embodiment)
In FIG. 5, the speed increasing link mechanism 51 and the like are the same as in the first embodiment, but the shearing section 31 shears a thin disk (single material 91X) from a strip-shaped plate (continuous material 90X). It is made possible. The fixed blade 32X has a hollow disk shape fixed to the die set 21 via a blank chamber 32XD, and the sub pressure block 61X includes a head 62 and a spring retainer 64, and holds the movable blade (punch 35X).

  The movable blade fixed position holding means 80X includes a spring 83 provided between the spring presser 64 and the punch guide 35XG, and returns the punch 35X to the fixed position shown in FIG. That is, according to this embodiment, the adaptability with respect to the morphological kind of the continuous material 90 and the single-piece material 91 is wide.

(Fourth embodiment)
In this embodiment (FIGS. 6 and 9), the basic configuration and function are the same as in the case of the first embodiment, but shearing region setting changing means 100 is further provided to shear the continuous material 90. Applicability to dimensional changes in the processing direction is formed to be expandable.

  That is, the shearing region setting changing means 100 is configured such that the driving node element (center of the driving node pin 55) connects the support pin 53 and the driven node element (center of the driving node pin 57) (X: see FIG. 6). It is mounted on the link lever 52 so as to be displaceable in the direction along the axis, and the range of the shearing region can be changed by adjusting the horizontal absolute position (shearing end position) of the driving node pin 55 with respect to the original pressure block 12 Is formed.

  In FIG. 6, the shearing region setting changing means 100 is formed of a taper guide member 109, a taper block 101, a position adjusting bolt 102, and the like.

  The taper guide member 109 has taper guide surfaces 109KL and 109KR that are separated in the axis (X) direction and form an upper narrow (lower wide) form, and are attached to the link lever 52L (and 52R) as a whole. . A movable auxiliary block 56BS is mounted between the tapered guide surfaces 109KL and 109KR so as to be displaceable (movable) in the X direction. The driving node pin 55 is fixed to the movable auxiliary block 56BS so as to be capable of synchronous displacement.

  The right vertical surface of the left taper block 101L engages with the left vertical surface of the movable auxiliary block 56BS, and the left taper surface 101KL engages with the taper guide surface 109KL. The left vertical surface of the right taper block 101R is engaged with the right vertical surface of the movable auxiliary block 56BS, and the right taper surface 101KL is engaged with the taper guide surface 109KL.

  The auxiliary plate 56PR attached to the link lever 56L (and 56R) is provided with female screw portions 56PRSL and 56PRSR that are screwed into the position adjusting bolts 102L and 102R. Adjusting operation portions 104L and 104R are provided at the base end portions of the position adjusting bolts 102L and 102R, and the distal end portions 103L and 103R are attached to the corresponding tapered blocks 101L and 101R so as to be rotatable and not vertically displaceable. Yes. Reference numeral 105 denotes a tightening nut, which is provided only on the position adjusting bolt 102L side in FIG. It may be provided on both sides.

  Thus, after loosening the tightening nut 105, the taper block 101L is raised (lowered) while operating the position adjusting bolt 102L using a hexagon wrench, and the taper block 101R is lowered (raised) while operating the position adjusting bolt 102R. ), The movable auxiliary block 56BS (primary node pin 55) can be displaced rightward (leftward).

  If the prime mover pin 55 is displaced leftward, the engagement release (separation) between the original pressure block 12 and the right end of the upper end surface 55U is accelerated. That is, the slide position (shear processing end position) Pil shown in FIG. 9 is increased. On the other hand, if the prime mover pin 55 is displaced rightward, the engagement release (separation) between the original pressure block 12 and the right end of the upper end surface 55U is delayed. That is, the slide position (shear processing end position) Pil shown in FIG. 9 is lowered. Therefore, since the slide position (shearing start position) Pih shown in FIG. 9 is constant, the range (stroke) [Pih to Pil] of the shearing region can be narrowed or widened.

  After the position adjustment, the tightening nut 105 is tightened to fix the position of the taper block 101L. Thereby, the position in the left-right direction of the movable auxiliary block 56BS (the driving node pin 55) and the tapered block 101P can be fixed.

  Therefore, according to this embodiment, in addition to the effects similar to those of the first embodiment, the adaptability to the dimensional change in the shearing direction of the continuous material 90 can be further expanded. When the diameter of the continuous material 90 is increased, the continuous material 90 can be completely cut by widening the stroke (Pih to Pil).

  In the first, second, and third embodiments, this shearing region setting change means 100 can be provided so that each shearing region (range) can be set and changed.

(Fifth embodiment)
In this embodiment (FIGS. 7 and 9), the basic configuration and function are the same as in the case of the first embodiment. However, the shearing start position setting changing means 110 is further provided to change the continuous material 90. The adaptability to the vertical set position change can be expanded.

  That is, the shearing processing start position setting changing means 110 is attached to the link lever 52 so that the driving node element (the driving node pin 55) can be displaced in the same direction as the downward movement direction of the original pressure block 12. By adjusting the absolute position in the vertical (Z) direction with respect to the original pressure block 12, the shearing start position that defines the shearing region can be set and changed.

  In FIG. 7, the taper block 111 that constitutes the shearing processing start position setting changing means 110 together with the position adjusting bolt 112 and the like has a taper surface 111K having a downward-rightward shape on the upper side, and is slidable on the auxiliary plate 56P as a whole. It is.

  The nut-attached block 119 attached to the link lever 52L (and 52R) is provided with a female screw portion 119S that is screwed with the position adjusting bolt 112. An adjustment operation portion 114 using a hexagon wrench is provided at the base end portion of the position adjusting bolt 112, and the distal end portion 113 is attached to the taper block 111 so as to be rotatable and not displaceable in the left-right direction. Reference numeral 115 denotes a tightening nut.

  The movable auxiliary block 56BS is provided with a tapered surface 56BSK corresponding to the tapered surface 111K of the tapered block 111 on the lower side, and relative displacement in the X direction of both 111K and 56BS is allowed when the position fixing bolts 117L and 117R are loosened, When tightening, relative displacement is impossible.

  Thus, after loosening the position fixing bolts 117L and 117R and then operating the position adjusting bolt 112 (114) to displace the taper block 111 in the right direction (left direction), the movable auxiliary block 56BS, that is, the driving node pin 55 (55U) can be raised (lowered). By raising (lowering) the drive node pin 55, the shearing start position Pih shown in FIG. 9 can be adjusted to the high position Piu (low position Pid).

  Thus, according to this embodiment, in addition to achieving the same effects as those of the first embodiment, the adaptability of the continuous material 90 to changes in the vertical set position can be expanded. That is, it is possible to immediately respond to specific changes in the vertical dimension and set position of the die set 21, continuous material 90, and blades (32, 35).

  In the first, second, third, or fourth embodiment, the shearing start position setting changing unit 110 may be provided so that each shearing start position (stroke) can be changed.

(Sixth embodiment)
In this embodiment (FIGS. 8 and 9), the configuration and function are the same as in the case of the first embodiment. Further, the shearing region setting changing unit 100 and the shearing start position setting changing unit 110 are further described. The area / position setting changing means 120 having both functions such as that constructed integrally is provided so that the adaptability to the dimensional change in the shearing direction and the vertical set position change of the continuous material 90 can be expanded. .

  The region / position setting changing means 120 is mounted with a movable body 56BS holding a driving node pin 55Y (upper end surface 55U) in a case 56BC integrally fixed to the auxiliary plate 56P so as to be displaceable in the horizontal and vertical directions. Adaptable to changes in dimensions in the shearing direction by changing the number of laterally moving shim members 122 inserted to the left and right of the movable body 56BS, and adaptable to changes in the vertical set position by changing the number of longitudinally moving shim members 121 inserted vertically. Is formed.

  That is, in FIG. 8, when the upper 2 and lower 2 longitudinally moving shim members 121 are set to upper 1 and lower 3, the movable auxiliary block 56BS (upper end surface 55U) can be raised by the thickness of one shim. Further, if the left and right 2 laterally moving shim members 122 are set to the left 1 and right 3, the movable auxiliary block 56BS (upper end surface 55U) can be displaced to the left by the thickness of one shim. .

  Therefore, according to this embodiment, compared with the case of the 4th and 5th actual form, further size reduction and handling property can be facilitated.

  Even if the movable pin member integrated with the drive node pin 55 is constructed so as to be movable in the arc-shaped groove provided on the auxiliary plate 56P side, both adjustments regarding the range of the shearing region and the shearing start position are performed simultaneously. Yes.

  In each of the above embodiments, the setting change of the range of the shearing region and the shearing processing start position is adjusted on the speed increasing link mechanism 51 side with respect to the original pressure block 12. On the other hand, the present invention can be applied even if it is constructed so as to be adjusted on the original pressure block 12 side.

  INDUSTRIAL APPLICABILITY The present invention is extremely effective for greatly simplifying the structure and reducing the size of a press machine having a shearing device.

It is a side view for demonstrating the 1st Embodiment of this invention, and shows the state just before the start of the shearing process of a continuous raw material (rod-shaped material). Similarly, a side view corresponding to FIG. 1 shows a state immediately after the end of shearing. Similarly, it is a rear view which shows the state seen from the left side of FIG. It is a side view for demonstrating the 2nd Embodiment of this invention, and shows the state just before the start of the shearing process of a continuous raw material (rod-shaped material). It is a side view for demonstrating the 3rd Embodiment of this invention, and shows the state just before the start of the shearing process of a continuous raw material (plate-shaped material). It is a figure for demonstrating the shear process area | region setting change means which concerns on the 4th Embodiment of this invention. It is a figure for demonstrating the shear processing start position setting change means based on the 5th Embodiment of this invention. It is a figure for demonstrating the area | region / position setting change means based on the 6th Embodiment of this invention. It is a figure for demonstrating the relationship between the slide motion of a press machine, a shear processing start position, etc. FIG.

Explanation of symbols

10 Press Machine 11 Slide 12 Original Pressure Block 21 Die Set (Main Body Block)
30 Shearing machine 31 Shearing part 32 Fixed blade (32U, 32D)
35 Movable blade (35U, 35D)
51 Speed increasing link mechanism (speed increasing transmission mechanism)
52 Link lever (52L, 52R)
53 Support Pin 55 Drive Node Pin (Drive Node Element)
56B Auxiliary block 56P Auxiliary plate 57 Follower pin (follower element)
58 driven roller 61 sub pressure block 75 material position regulating member 80 movable blade fixed position holding means 90 continuous material 91 single material 100 shearing region setting changing means 101 taper block 102 left and right position adjustment bolt 109 taper member block 110 shearing processing start position Setting change means 111 Height adjustment block 112 Position adjustment bolt 114 Adjustment operation unit 119 Block with nut 120 Area / position setting change means

Claims (6)

A press machine having a shearing device for forming a single material for press processing from a continuous material by shearing,
A shearing device including a fixed blade fixed to the main body block and a movable blade mounted so as to be movable up and down with respect to the fixed blade; Including a link lever having a drive node element closer to the support pin mounted on the main body block and a follower node element far away from the support block, the speed increase function capable of rotating about the support pin as a whole and expressing the speed increasing function A link mechanism, an original pressure block attached to the slide so as to be able to transmit an original pressure applied by the downward movement of the slide to the link lever while being engaged with the drive node element, and a link lever of the link lever being engaged with the follower element In the shearing region where the original pressure block and the driving node element are engaged, the slide lowering movement can be performed. The follower element can be increased to a speed faster than the slide descent speed by the interlocking movement of the speed increasing link mechanism, and the follower applied to the movable blade from the follower element that descends at a high speed after the acceleration. A press machine provided with a shearing device that is formed so as to be capable of shearing using pressure.   The prime mover element is mounted on the link lever so as to be displaceable in a direction along an axis connecting the support pin and the follower joint element, and adjusts the absolute position of the prime mover element in the horizontal direction with respect to the primary pressure block. The press machine comprising the shearing device according to claim 1, wherein the shearing region can be set and changed.   The prime mover element is mounted on the link lever so as to be displaceable in the same direction as the downward movement direction of the prime pressure block, and by adjusting the absolute position of the prime mover element in the direction perpendicular to the prime pressure block The press machine provided with the shearing device according to claim 1 or 2, wherein the shearing processing start position defining the shearing region can be set and changed.   The plurality of speed increasing link mechanisms are brought into an engageable state with the driving link element of the speed increasing link mechanism in which the driven link element of the front speed increasing link mechanism is placed rearward, and the original pressure block and the follower A press machine comprising the shearing device according to any one of claims 1 to 3, wherein the press machine is arranged in series with a pressure block.   The link lever is formed of a pair of link lever elements arranged to face the support pin, and the upper side of the driving node pin forming the driving node element has a planar shape facing the lower end surface of the original pressure block. A press machine comprising the shearing device according to any one of claims 1 to 4, wherein a lower side thereof is integrally locked with an auxiliary block provided between both link lever elements.   The press machine provided with the shear processing device according to any one of claims 1 to 5, wherein the main body block is formed of a die set or a die set plate.

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