EP2158074A1 - Presse de découpage - Google Patents

Presse de découpage

Info

Publication number
EP2158074A1
EP2158074A1 EP08757284A EP08757284A EP2158074A1 EP 2158074 A1 EP2158074 A1 EP 2158074A1 EP 08757284 A EP08757284 A EP 08757284A EP 08757284 A EP08757284 A EP 08757284A EP 2158074 A1 EP2158074 A1 EP 2158074A1
Authority
EP
European Patent Office
Prior art keywords
crankshaft
punching press
press according
lever
tension
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP08757284A
Other languages
German (de)
English (en)
Other versions
EP2158074B1 (fr
Inventor
Josef Thomas Hafner
Ugo De Santis
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bruderer AG
Original Assignee
Bruderer AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bruderer AG filed Critical Bruderer AG
Priority to EP08757284.8A priority Critical patent/EP2158074B1/fr
Publication of EP2158074A1 publication Critical patent/EP2158074A1/fr
Application granted granted Critical
Publication of EP2158074B1 publication Critical patent/EP2158074B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/02—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by lever mechanism
    • B30B1/06—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by lever mechanism operated by cams, eccentrics, or cranks
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/26—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks
    • B30B1/263—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks work stroke adjustment means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/0029—Details of, or accessories for, presses; Auxiliary measures in connection with pressing means for adjusting the space between the press slide and the press table, i.e. the shut height
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/04—Frames; Guides
    • B30B15/041—Guides

Definitions

  • stamping presses with a drive mechanism arranged below the punching plane and connected via tension columns to the press ram have proven to be particularly suitable for the industrial production of demanding stamped parts, since such punch presses, in particular in embodiments in which the press ram connected at each of its four outer corners with a Switzerlandchule, a maximum tilting stiffness both in the direction of passage and at right angles to achieve.
  • a press is the punching machine type BSTA 60 from Bruderer AG, CH-Frasnacht, mentioned, from which since 1965 more than 1100 pieces were built.
  • two of the four tension columns each are driven by a common crank drive, in that the crank shaft-remote end of the connecting rod of the crank mechanism is articulated directly on a yoke rigidly connecting the two tension columns.
  • this machine concept can no longer fully meet all requirements, in particular with a further increase in the maximum punching frequency or operation with a highly eccentric Load on the ram a disproportionately increasing component load and concomitantly a corresponding wear or a correspondingly increasing maintenance intensity preclude.
  • the invention relates to a punch press with a fixed platen and one of the top of the platen opposite and working against the platen press ram.
  • the stationary tool part of a punching tool to be operated with the punch press is carried by the upper side of the clamping plate, while the moving tool part is carried by the press ram.
  • the press ram is driven by tension columns, which serve to transmit the driving forces on the press ram, with a arranged below the punch plane drive mechanism such that it performs the required for the punching operation upward and downward movement.
  • the guide of the press ram is carried out exclusively via the preferably rigidly connected thereto tension columns, which are guided in the structure of the punching press vertically displaceable in guides.
  • the guides are such that an inclined position of the press ram and the tension pillars caused by an eccentric load attack on the ram can be effected by an inclination of the tension pillars around tilt axes extending in the region of the strip running plane.
  • area of the strip running plane is understood to mean an area between 40 mm above and 40 mm below an ideal or middle strip running plane can be achieved, for example, by using a single inclination-tolerant guide per tension column whose inclination axes run in the region of the strip running plane or by using two spaced-apart guides per traction column, which are accommodated in the press structure in such a way that they are common can incline around tilting axes running in the region of the strip running plane.
  • the embodiment according to the invention avoids distortion of the punching press under eccentric load, which would lead to uncontrollable operating conditions and high wear.
  • a significant bending stress of the tension columns is possible in this construction only in rigid execution of the connection between press ram and tension column and is also limited to the transition point between tension column and press ram, where this bending stress is not a problem.
  • the embodiment according to the invention also ensures that, in the event of a ram tilt, no tool offset occurs which could result in high tool wear or even tool breakage. Accordingly, punching presses can be made available by the invention which combine minimal wear, both on the machine side and on the tool side, with maximum punching precision, even with eccentric loading.
  • the tension columns are guided exclusively in the region of the strip running plane of the punch press, preferably in the ideal or middle strip running plane of the punch press, preferably in tilt-tolerant guides which, moreover, are preferably essentially torque-free.
  • tilt-tolerant guides here guides are understood, which by their structural design an inclined position of the tension column relative to the neutral guide axis, which Usually the vertical is to allow at least 0.05 °, preferably at least 0.10 °, without resulting in damage or a significantly increased wear.
  • Such bearings are considered essentially torque-free if they oppose substantially no forces to the inclination.
  • two mutually opposite tension columns are rigidly connected to one another via a connecting element, such as, for example, via a yoke.
  • a connecting element such as, for example, via a yoke.
  • connection between the press ram and the tension columns is also rigid, so that the press ram, the tension columns and the connecting element form a substantially angularly rigid frame structure in the plane formed by the longitudinal axes of the tension columns as a whole can perform a tilting movement.
  • the punch press has exactly four tension columns, which are each arranged at the corners of the press ram. This allows a maximum tilting stiffness reach speed of the plunger both longitudinally and transversely thereto.
  • the drive mechanism of the punch press comprises means for compensating a load-related elongation of the tension columns, preferably for individual compensation of a load-related elongation of each train column, so that a correction of occurring under eccentric load during operation different elongations of the tension columns and the concomitant misalignment of the press ram is possible. Because of the design of the press according to the invention, this also makes it possible, for example, to adjust the punch press for operation with eccentric ram loading in such a way that the press ram is tilted without a load but is straight under load.
  • the drive mechanism has at least one crankshaft with one or more connecting rods arranged on one or more crankpins of the crankshaft, with which a rotational drive movement provided by a drive motor can be intermittently moved upwards and downwards Drive can be converted by at least one tension column of the press ram.
  • the Crankshaft so the drive only a train column, the drive of several tension columns or the drive all tension columns of the punch press are used.
  • Such Antriebskon ⁇ scepter have proven themselves in the field of stamping presses and systemically have an advantageous punching force curve. Also results due to the harmonious motion sequences a long life of highly stressed components.
  • the at least one crankshaft runs in the longitudinal direction of the stamping press, ie in the strip running direction, wherein it is further preferred that exactly one crankshaft running in the longitudinal direction is present for driving all tension columns.
  • crankshaft is arranged centrally along the longitudinal axis of the punch press, such that a symmetrical arrangement results with respect to the tension pillars. This results in the advantage of a symmetrical distribution of forces in the entire press assembly, which can be on the drive side optimal conditions for maximum parallelism of platen and ram to ensure under load.
  • crankshaft has exactly two crankpins, which are preferably each arranged in the region of one end of the crankshaft and at least on the side facing away from the respective shaft end of a crankshaft associated with this Preferably designed as a rolling bearing radial bearings of the crankshaft are flanked.
  • crankpins which are preferably each arranged in the region of one end of the crankshaft and at least on the side facing away from the respective shaft end of a crankshaft associated with this Preferably designed as a rolling bearing radial bearings of the crankshaft are flanked.
  • crank pin are each flanked on both sides by a respective crank pin, preferably designed as a rolling bearing radial bearing of the crankshaft, so that an introduction of bending moments in the crankshaft is substantially avoided.
  • crankshaft in the region between the radial bearings, which are each arranged on the side facing away from the shaft end of the respective crank pin, is designed as a hollow shaft.
  • crankshaft be constructed as, i.e. composite shaft is formed, in such a way that the part formed as a hollow shaft is formed as a separate component from the crank pin.
  • the crankshaft be constructed as, i.e. composite shaft is formed, in such a way that the part formed as a hollow shaft is formed as a separate component from the crank pin.
  • crankshaft is designed such that the lifting height of its crank pin is adjustable. It is further preferred that the crankshaft has crankpins, which are each formed by an eccentric cam and an eccentric bush rotatably arranged on it, such that different elevation heights are achieved by turning the eccentric bushing on the eccentric the crankshaft are adjustable. This results in the advantage of the adjustability of the lifting height.
  • crankshaft is designed as a hollow shaft in the area between those radial bearings, which are respectively arranged on the side of the respective crank pin facing away from the shaft end, which is preferred, then it is further preferred for the locking means to have a central position Loosening mechanism are releasable, which extends through the interior of the hollow shaft formed as part of the crankshaft.
  • the crankshaft is mounted in radial bearings, wherein exactly one of the radial bearings of the crankshaft is designed as a fixed bearing for receiving the forces acting on the crankshaft axial forces.
  • the drive mechanism of which has at least one crankshaft with one or more associated connecting rods the crankshaft is mounted in radial bearings, which are each assigned to one of the crankpins and are arranged in a separate crankpin. Housing part are mounted, which is in each case connected to a central, the platen bearing or forming housing part, preferably by screwing.
  • each connecting rod is articulated at a first end of a lever or at respective first ends of a plurality of levers, which lever on their second ends are hinged directly or indirectly to the structure of the punch press, for example by means of a stationary mounted on the housing of the punch press support pin (directly), or eg via a housing attached to the punch press support assembly with an adjustable relative to the housing articulation point for the lever and / or via a tab (indirect).
  • the articulation is such that the lever or levers can be pivoted back and forth about its second end by rotating the crankshaft by means of the connecting rod.
  • the lever or the levers are each connected in an area between the first and the second end hingedly connected to at least one tension column of the punch press, such that the tension column can be moved up and down by swinging the respective lever back and forth.
  • This embodiment of the stamping press has the advantage that a division of the thrust driving forces results, whereby the bearing load of the crankshaft is significantly reduced, which in turn a high durability of the press (low wear) and a high precision even at high punch frequencies zulut is. Due to the reduction of the stroke movement generated by the crank mechanism in the lever mechanism of the press, This embodiment is particularly suitable as a "short stroke press".
  • the respective lever is hinged at its second end via a tab indirectly to the structure of the punch press. Is This results in the advantage that essentially only vertical forces on this ⁇ nlenk Vietnamese can be transmitted to the structure, so that share a Bie ⁇ gebe pipeung of the articulation point forming construction substantially avoided.
  • the articulation point is formed by an adjustable support arrangement, for example by a threaded spindle with which the vertical position of the Anlenk- kungsembls is adjustable.
  • the respective lever is connected in the region between the first and the second end via a tab with the tension column. This results in a horizontal mobility with the additional advantage that essentially only vertical forces can be transmitted via this pivot point.
  • crankshaft remote end of the respective connecting rod form a common pivot point with the first ends of two opposite, seen in the crankshaft longitudinal direction mirror image arranged lever, which preferably in crankshaft longitudinal direction seen in Spie gelsentaji way are each assigned to a train column.
  • the drive mechanism having at least one crankshaft with one or more associated connecting rods, the crankshaft remote end of each connecting rod is connected to a first end of at least one lever which hinged in an area between its first and its second end to the structure of the punch press is, for example by means of a support pin immovably mounted on the housing of the punch press (direct), or e.g. via a support arrangement fastened to the housing of the stamping press with an articulation point for the lever which can be adjusted relative to the housing and / or via a tab (indirectly).
  • the linkage is such that the lever can be pivoted back and forth about its articulation point by rotating the crankshaft through the connecting rod, wherein the lever is pivotally connected at its second end to at least one tension column of the punch press, such that the Pull column can be moved by swinging back and forth of the lever up and down.
  • This refinement of the stamping press has the advantage that due to the sweeping of the movements via the lever, a certain compensation of the moving masses already takes place due to the system, so that only small additional compensating masses are required. Also, a ratio of crank stroke to ram stroke of 1: 1 or greater can be realized in a simple manner, which is why this embodiment is particularly suitable as a "long-stroke press".
  • the respective lever in a region between its first and its second end is preferably articulated directly by means of a pivot axis forming bolt directly to the structure of the punch press, so that both vertical and horizontal forces can be transmitted to the structure via this point of articulation.
  • the respective lever is connected at its second end via a tab to the tension column. This results in a horizontal mobility with the additional advantage that essentially only vertical forces can be transmitted via this articulation point.
  • crankshaft remote end of the respective connecting rod is guided vertically, such that this is movable exclusively in the vertical direction.
  • the crank-shaft-distal end of the connecting rod which is thus determined horizontally, is connected to the first end of the at least one lever via a lug.
  • crankshaft remote end of the respective connecting rod via sepa ⁇ rate tabs at the first ends of two opposing, horizontally fixed, seen in the crankshaft longitudinal direction mirror image arranged lever is hinged, which preferably in crankshaft longitudinal direction in a mirror image each one Glascicle are assigned. This results in the pre ⁇ part of a compact design and a zwangsssynchronen drive two Anlagenrochlen.
  • the means for compensating the load-related elongation of the tension columns are designed such that with them the position and preferably the vertical position of the articulation point of the respective lever is adjustable to the structure of the punch press, preferably during the punching operation of the press.
  • the position of the articulation point of the respective lever on the structure of the punch press can be adjusted by means of a threaded spindle, preferably with the aid of a servomotor driving the threaded spindle.
  • the position of the articulation point of the respective lever on the structure of the punch press by means of a servomotor, preferably with planetary gear, rotatable eccentric is adjustable.
  • each lever is associated with exactly one tension column, preferably, that the vertical positions of the articulation points of the levers are groupwise or independently adjustable.
  • Such preferred embodiments of the stamping presses therefore have several levers according to the claims, at or at the first ends of which the crank shaft remote end of a connecting rod is articulated or connected, wherein the levers are articulated directly or indirectly to the structure of the stamping press such that the respective one Lever by rotating the crankshaft by the connecting rod around its articulation point around and can be swung back and forth.
  • the levers are each, optionally via articulation on a two tension columns connecting yoke, hingedly connected to a respective lever associated with the tension column of the punch press, such that the tension column can be moved by swinging back and forth of the lever up and down.
  • the punch press is designed such that the vertical positions of the articulation points of the levers are groupwise or independently adjustable.
  • FIG. 2 shows a longitudinal section along the line B-B in FIG. 1;
  • Fig. 3 is a plan view of the punch press of Figures 1 and 2 with the press ram removed;
  • FIGS. 1 to 3 shows two horizontal sections through one of the two machine housings of the stamping press from FIGS. 1 to 3 with different variants of spindle drives for the ram height adjustment;
  • FIG. 5a shows a vertical section through one of the plunger guides along the line F-F in Fig. 3 and Fig. 5b.
  • Fig. 5b is a horizontal section through one of the ram guides along the G-G in Fig. 2 and Fig. 6;
  • FIG. 6 shows a cross section through a second punching press according to the invention along the line C-C in FIG. 7;
  • Figure 1 is a longitudinal section along the line D-D in Fig. 6.
  • FIGS. 1 to 4 show a cross section (FIG. 1), a longitudinal section (FIG. 2) and horizontal sections through one of the machine housings (FIG. 4) of the stamping press, and FIG Top view of the punch press with removed press ram (Fig. 3).
  • the basic structure of the stamping press consists of two machine housings 15, 15b, and a cross member 15a with a clamping plate 23, which are connected to one another by means of screws 15d.
  • a press ram 1 is arranged, which is rigidly connected to four tension pillars 2 each arranged at its outer corners.
  • Each two of the tension columns 2 are respectively associated with one of the two machine housings 15, 15b, which also contain the drive mechanism described below for the respective tension columns 2, and are mounted vertically displaceably in guides 3 in these, the guides 3 being incorporated in guide posts are that simultaneously form parts of the housing cover 4 of the respective machine housing 15, 15b.
  • 15b associated tension columns 2 are in the machine housing 15, 15b at their end facing away from the plunger 1 each rigidly connected via a transverse yoke 5, which in turn is articulated with two tabs 6 via bolts 6a hinged to four levers 7.
  • the press center facing the ends of the lever 7 are by means of a common connecting rod with two independent connecting rods 8 connected.
  • the upper ends of the connecting rods 8 perform during operation a lifting movement and are guided with sliders 21 in linear guides 22, such that the connecting rod can perform only a vertical movement.
  • the punch press can be set to a number of precisely defined lifting heights by fixing different relative angular positions between the eccentric bush 9 and the eccentric 10 with a locking bolt 32 in a form-fitting manner.
  • the locking pin 32 is unlocked with a release mechanism 31 for Hubcicn.
  • the crankshaft 9, 10, 29 consists of the two respective end side arranged on this crank pin 9, 10 and a hollow shaft 29 which connects the crank pin 9, 10 with each other and is protected by a cover 15c. It is mounted with three movable bearings 30 and a fixed bearing 33 in the two machine housings 15, 15b.
  • the release mechanisms 31 are connected to each other via a coupling shaft 28 extending in the center of the hollow shaft 29 and thereby actuatable together from that side of the punch press which has the fixed bearing 33.
  • the drive assemblies 27 such as brake, clutch ment and flywheel with the crankshaft 9, 10, 29 arranged.
  • a mass balance lever 16 In order to realize a balance of the moving masses, the front end of a mass balance lever 16 is hinged to each bolt 6a, in each case in addition to the tab 6. The center of this lever 16 is rotatably supported in a bolt fixed to the housing. The rear end of the lever 16 is pivotally connected to a counterweight 14 and drives this in operation in the opposite direction of the bumps 1. The mass forces in the stroke direction are compensated in this way. Furthermore, push rods 11 are present, which are arranged on the underside of the respective connecting rod 8 and via levers 13 drive the counterweights 14 in the opposite direction of the connecting rod 8, to compensate for the horizontal dynamic forces.
  • Fig. 3 shows a plan view of the punch press with removed press ram 1.
  • the four tension columns 2 are shown in section.
  • an adjusting mechanism 35 with a servo motor 34 for the adjustment and, if necessary, regulation of the position of the articulation point of the respective lug 7a is present for each tension column 2.
  • the respective servo-gear motor unit 34, 35 drives for adjustment via a worm 36 to the respective worm wheel 18, which is an integral part of the threaded spindle 19.
  • Fig. 4 shows a horizontal section through one of the two machine housing 15, 15b of the punch press of Figures 1 to 3. If only eccentric loads in the longitudinal direction of the machine are expected, a variant with only one gear motor 34, 35 per machine housing 15, 15b is provided, as shown in the right half of Fig. 4. As can be seen, only two motor-gear units 34, 35 are used in this case for the four tension columns 2, wherein each of the arranged in a common machine housing 15, 15b screws 36 are rotatably connected to a hollow shaft 24.
  • FIGS. 5a and 5b show sections through one of the guide supports, wherein FIG. 5a shows a vertical partial section through the guide support along the line FF in FIG. 3 or FIG. 5b and FIG. 5b shows a horizontal section along the GG in FIG
  • each of the four columns 2 in the guide support is guided from two sides with oil-flowed round sliding shoes 50. From the tension column 2 opposite side of this shoe 50 is provided with a hemispherical bore. Depending on a nut 51 with a spherical end of the game setting or readjustment of the same.
  • the lid 52 on the one hand, the lubricating oil is fed and on the other hand, the adjusting nut 51 countered.
  • FIGS. 6 to 8 show a cross section through the stamping press (FIG. 6), a longitudinal section through one half of the stamping press (FIG. 7) and a section through one half of the lever mechanism a press side (Fig. 8) show.
  • FIGS. 6 to 8 show a cross section through the stamping press (FIG. 6), a longitudinal section through one half of the stamping press (FIG. 7) and a section through one half of the lever mechanism a press side (Fig. 8) show.
  • the basic structure of the stamping press consists of two machine housings 15 (Here, only a machine housing is shown) and a cross member 15a with a platen 27, which are interconnected by means of screws. Above the platen 27, a press ram 1 is arranged, which is rigidly connected to four (only two visible) each arranged at its outer corners tension columns 2.
  • Each two of the tension columns 2 are in each case one of the two machine housings 15, each of which receives the drive mechanism described below for the respective tension columns 2, assigned and vertically slidably guided in guides 3, which are identical to those used in the first embodiment and in the figures 5a and 5b are shown in detail guides.
  • the guides in the ideal or middle strip level X in the respective machine housing 15 are also arranged here, also by being installed in guide supports of the housing cover 4 of the respective machine housing 15. Furthermore, here are the two a common machine housing 15th associated Wegchulen 2 in the machine housing 15 at their ends facing away from the ram 1 rigidly connected together via a yoke 5.
  • Each yoke 5 is articulated in turn with tabs 6 via bolts hinged to the opposite ends of the press center two mirror-inverted opposite levers 7, 7a.
  • the levers 7, 7a are each pivotally mounted in the machine housing 15 in the middle between their two ends with a housing-fixed eccentric shaft 8, 8a.
  • the eccentric shafts 8, 8a are driven in the housing 15 by means of servomotors with planetary drives (partially shown in FIG. 8), whereby the position of the articulation points of the levers 7, 7a on the structure can be changed.
  • the press center facing the ends of these levers 7, 7a are each connected via a bolt with a pressure tab 18, 18a hinged, which in turn articulated via a common bolt each with the crankshaft remote end of an independent connecting rod 16, 16a are connected.
  • the upper ends of the connecting rods 16 perform during operation a lifting movement and are each guided with sliding blocks 17 in linear guides 17a, such that the common connecting rod can perform only a vertical movement.
  • the remaining balance of moving masses is realized here by the fact that the outer ends of the pressure plates 18, 18 a are each hingedly connected to the upper end of a balance weight 14. As a result, mass forces are compensated in the stroke direction. Furthermore, push rods 11 are present, which are arranged on the underside of the respective connecting rod 16, 16a and via levers 13 drive the counterweights 14 in the opposite direction of the connecting rod 16, 16a, to compensate for the horizontal dynamic forces.
  • levers 7, 7a overlap in the press center, where they each have bolts and the pressure plate 18 associated therewith , 18a, at the crankshaft remote end of the associated connecting rod 16, 16a are articulated.
  • the press center facing away from the end of the lever 7, 7a are articulated in each case via bolts and their associated pull tabs 6 on the transverse yoke 5 of the tension columns 2.
  • the levers 7, 7a each pivotally mounted on their associated eccentric shaft 8, which is mounted at its two ends in the housing 15.
  • the eccentric shafts 8 in turn can each be rotated about their bearing points by means of a servo motor with planetary gear 20, 21, 22, 23, whereby the pivoting center of the respective lever 7, 7a relative to the housing 15 can be changed and thus the articulation point of the respective lever 7 , 7a on the housing 15.
  • This has the consequence that the distance of the lower edge of the plunger 1 to the upper edge of the platen 27 can be adjusted. This can be discussed on different tool heights, or you can correct the position of the bottom dead center of the ram 1. Also, this makes it possible to correct a misalignment of the ram 1 under eccentric load.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Presses And Accessory Devices Thereof (AREA)

Abstract

L'invention concerne une presse de découpage comprenant un plateau de serrage (27) et un coulisseau de presse (1) opposé au côté supérieur du plateau de serrage (27) et travaillant contre le plateau de serrage (27), qui peut être déplacé de haut en bas par le biais de quatre colonnes de traction (2) avec un mécanisme de bielles disposé sous le plan d'avance de bande (X) de la presse de découpage. Le coulisseau de presse (1) est guidé exclusivement par le biais des colonnes de traction (2), qui sont à leur tour guidées dans des coulisses (3) à tolérance d'inclinaison dans le plan d'avance de bande (X), de telle sorte qu'une position en biais du coulisseau de presse (1) et des colonnes de traction (2) résultant d'étirements longitudinaux différents des colonnes de traction (2) sous l'effet d'une charge excentrée est possible par l'inclinaison des colonnes de traction (2) autour d'axes d'inclinaison s'étendant dans la région du plan d'avance de bande (X) de la presse de découpage. Grâce à la configuration selon l'invention, on évite un gauchissement de la presse de découpage sous l'effet d'une charge excentrée, qui conduirait à des conditions de fonctionnement non maîtrisables lors du découpage, et à une usure élevée au niveau des coulisses de la machine, et on peut en outre garantir que, dans le cas d'un éventuel positionnement en biais du coulisseau, il ne se produit aucun décalage d'outil, qui conduirait à une grande usure de l'outil voire à une rupture de l'outil.
EP08757284.8A 2007-06-28 2008-06-26 Presse de découpage Active EP2158074B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP08757284.8A EP2158074B1 (fr) 2007-06-28 2008-06-26 Presse de découpage

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP07012661A EP2008799A1 (fr) 2007-06-28 2007-06-28 Presse à découper
EP08757284.8A EP2158074B1 (fr) 2007-06-28 2008-06-26 Presse de découpage
PCT/CH2008/000291 WO2009000100A1 (fr) 2007-06-28 2008-06-26 Presse de découpage

Publications (2)

Publication Number Publication Date
EP2158074A1 true EP2158074A1 (fr) 2010-03-03
EP2158074B1 EP2158074B1 (fr) 2020-04-29

Family

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Family Applications (2)

Application Number Title Priority Date Filing Date
EP07012661A Withdrawn EP2008799A1 (fr) 2007-06-28 2007-06-28 Presse à découper
EP08757284.8A Active EP2158074B1 (fr) 2007-06-28 2008-06-26 Presse de découpage

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP07012661A Withdrawn EP2008799A1 (fr) 2007-06-28 2007-06-28 Presse à découper

Country Status (7)

Country Link
US (1) US8739595B2 (fr)
EP (2) EP2008799A1 (fr)
JP (1) JP5526024B2 (fr)
CN (1) CN101687379B (fr)
ES (1) ES2798003T3 (fr)
SG (1) SG157194A1 (fr)
WO (1) WO2009000100A1 (fr)

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* Cited by examiner, † Cited by third party
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CN101905544A (zh) * 2010-07-28 2010-12-08 扬州捷迈锻压机械有限公司 一种高强度液压机导向立柱
DE102011052860A1 (de) 2010-08-24 2012-03-01 Schuler Pressen Gmbh Verfahren zum Betreiben einer Presse mit Unterantrieb und danach betriebene Presse
LT5880B (lt) 2011-03-04 2012-11-26 Liudvikas Vitalijus ORÅŖNAS Rotorinis variklis
DE102012100325C5 (de) 2012-01-16 2019-06-19 Schuler Pressen Gmbh Verwendung von Daten des Kraftflusses in einer Presse für den Betrieb eines Stößels
DE102012108933B4 (de) * 2012-09-21 2019-08-08 Schuler Pressen Gmbh Verfahren zum Betreiben einer Werkzeugmaschine oder Arbeitsmaschine und danach ausgeführte Werkzeugmaschine oder Arbeitsmaschine mit einer Verbindungsanordnung für ein Hubelement
GB2507068B (en) * 2012-10-17 2015-06-03 Tg Can Ip Ltd Press for a cupping system
GB2507065B (en) * 2012-10-17 2015-12-23 Tg Can Ip Ltd Press for a cupping system
CN102975386B (zh) * 2012-11-27 2014-12-17 南京理工大学 能实现下死点动态精度补偿的高速精密数控冲床机构
CN103240379B (zh) * 2013-05-13 2015-10-21 天津市万华车料有限公司 辐条机条帽球面成型模调整结构
US20160144588A1 (en) * 2013-06-19 2016-05-26 Bruderer Ag Method for warping the machine bed and/or the press ram of a punching press and punching press
CN107309313B (zh) * 2017-07-07 2019-02-19 浙江玛德机械有限公司 简易小冲床
CN108000919B (zh) * 2018-01-22 2024-04-26 东莞领益精密制造科技有限公司 台式小型电动冲床
EP4073767A4 (fr) 2019-12-10 2024-01-31 Barnes Group Inc. Capteur sans fil à technologie de balise
WO2021144012A1 (fr) 2020-01-15 2021-07-22 Bruderer Ag Procédé de fonctionnement d'une presse à estamper et presse à estamper pour le fonctionnement selon le procédé
CN113118371B (zh) * 2021-04-15 2023-03-31 辽宁五一八内燃机配件有限公司 一种模锻压力机的曲轴锻件翻转装置
US12214567B2 (en) 2021-09-08 2025-02-04 PDInnovative LLC Press machine having planetary gear system for multi-speed drive functionality
US11919267B2 (en) 2021-09-21 2024-03-05 PDInnovative LLC Linear-actuated press machine having telescopic drive configuration for multi-speed drive functionality
US11819906B2 (en) 2021-09-21 2023-11-21 PDInnovative LLC Linear-actuated press machine having multiple motors and clutch system for multi-speed drive functionality
CN115815455B (zh) * 2022-11-25 2026-02-06 东莞市泰基山机械设备有限公司 下拉式高速冲床

Family Cites Families (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2120356A (en) * 1936-09-04 1938-06-14 Rudolph W Glasner Press
GB557297A (en) * 1942-05-15 1943-11-15 Walter Samuel Wilkins Improvements in power presses
US2544540A (en) 1948-02-17 1951-03-06 Hedwig Maust Underdrive punch press
US2696165A (en) * 1950-10-04 1954-12-07 Otto Hermann May Toggle press
LU37958A1 (fr) * 1959-02-06
CH427442A (de) 1965-12-02 1966-12-31 Bruderer Ag Vorrichtung für den Massenausgleich bei durch Kurbeltrieb angetriebenen Maschinen
CH541418A (de) * 1971-08-04 1973-09-15 Maschb Ing O Klammer Verfahren und Einrichtung zur Verstellung der Lage des Stösselhubes bei Pressen
CH568848A5 (fr) 1974-08-29 1975-11-14 Bruderer Ag
US4160409A (en) * 1974-09-03 1979-07-10 Bruderer Ag Drive for the movable work component, such as the ram of a press, stamping machine or the like
CH581281A5 (fr) * 1974-09-03 1976-10-29 Bruderer Ag
US4238950A (en) * 1979-04-09 1980-12-16 Gulf & Western Manufacturing Company Bolster arrangement for opposed slide double acting press
US4397232A (en) 1981-09-08 1983-08-09 The Minster Machine Company Mechanical press having a drop in drive assembly
JPS58119494A (ja) * 1982-01-11 1983-07-15 ロマン・ミハイロウイツチ・アデニン 下方駆動型プレス
DE3422644A1 (de) * 1984-06-19 1985-12-19 SMS Hasenclever Maschinenfabrik GmbH, 4000 Düsseldorf Schmiedepresse in unterflurbauart
JPS629728A (ja) * 1985-07-08 1987-01-17 Kazuhito Fukazawa カムシヤフトの製造方法
JPS6228100A (ja) * 1985-07-29 1987-02-06 Sugiyama Chain Seisakusho:Kk プレス機のカウンタバランス装置
JPS6325389A (ja) 1986-07-18 1988-02-02 Yamada Denki Seizo Kk 流量圧力制御装置
CH677336A5 (fr) 1988-08-31 1991-05-15 Bruderer Ag
EP0360875B1 (fr) * 1988-09-02 1991-05-29 Gräbener Pressensysteme GmbH & Co. KG Machine de formage, notamment presse mécanique
CH684394A5 (de) 1991-12-11 1994-09-15 Bruderer Ag Einwellen-Stanzpresse.
US5458057A (en) * 1992-12-21 1995-10-17 Arens; Cornelius G. Apparatus for facilitating the installation of a dieset in a reciprocating press
JPH07164198A (ja) * 1993-12-13 1995-06-27 Yamada Dobby Co Ltd ダイイングマシン
DE59500682D1 (de) * 1995-01-21 1997-10-23 Bruderer Ag Stanzpresse mit langem Werkzeugeinbauraum
EP0765735B1 (fr) 1995-09-27 2001-04-11 Bruderer Ag Presse poinçonneuse à genouillère
US5852970A (en) 1995-11-27 1998-12-29 The Minster Machine Company Underdrive opposing action press
EP0927630B1 (fr) 1997-12-12 1999-09-08 Bruderer Ag Presse, en particulier presse à estamper
EP0953438B1 (fr) 1998-04-30 2005-03-02 Bruderer Ag Presse à estamper, en particulier presse rapide
DE19821159A1 (de) 1998-05-12 1999-11-25 Johannes Huelshorst Tiefziehpresse
US6170392B1 (en) 1998-11-18 2001-01-09 The Minster Machine Company Upper slide drive rod and spacer design
JP4404984B2 (ja) * 1999-03-24 2010-01-27 株式会社山田ドビー プレス機
US6477945B1 (en) 1999-09-07 2002-11-12 Aida Engineering, Ltd. Double-action mechanical press
JP3667227B2 (ja) * 2000-11-13 2005-07-06 株式会社山田ドビー プレス機

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2009000100A1 *

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Publication number Publication date
CN101687379A (zh) 2010-03-31
EP2008799A1 (fr) 2008-12-31
JP2010531234A (ja) 2010-09-24
CN101687379B (zh) 2014-11-12
US8739595B2 (en) 2014-06-03
JP5526024B2 (ja) 2014-06-18
US20100206187A1 (en) 2010-08-19
ES2798003T3 (es) 2020-12-04
EP2158074B1 (fr) 2020-04-29
WO2009000100A1 (fr) 2008-12-31
SG157194A1 (en) 2009-11-30

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