EP2158074A1

EP2158074A1 - Punching press

Info

Publication number: EP2158074A1
Application number: EP08757284A
Authority: EP
Inventors: Josef Thomas Hafner; Ugo De Santis
Original assignee: Bruderer AG
Current assignee: Bruderer AG
Priority date: 2007-06-28
Filing date: 2008-06-26
Publication date: 2010-03-03
Anticipated expiration: 2028-06-26
Also published as: JP2010531234A; CN101687379B; WO2009000100A1; SG157194A1; CN101687379A; US20100206187A1; ES2798003T3; EP2158074B1; JP5526024B2; US8739595B2; EP2008799A1

Abstract

The invention relates to a punching press with a clamping plate (27) and with a press ram (1) which lies opposite the upper side of the clamping plate (27) and operates towards the clamping plate (27) and is moveable up and down via four tension columns (2) by means of a crank drive arranged below the belt movement plane (X) of the punching press. The press ram (1) is guided exclusively via the tension columns (2) which, in turn, are guided in inclination-tolerant guides (3) in the belt movement plane (X) in such a manner that the press ram (1) and the tension columns (2) can be positioned obliquely as a consequence of differing longitudinal expansion of the tension columns (2) under an eccentric load by the tension columns (2) being inclined about axes of inclination running in the region of the belt movement plane (X) of the punching press. By means of the configuration according to the invention, distortion of the punching press under an eccentric load, which would lead to uncontrollable operating conditions during the punching and a high degree of wear at the guides of the machine, is avoided, and it can be ensured that, in the event of a possible skewed position of the ram, no tool offset, which would result in a high degree of tool wear or even in tool fracture, occurs.

Description

punch press

CROSS-REFERENCE TO RELATED APPLICATIONS This application claims priority to European Patent Application No. 07 012 661.0 filed on Jun. 28, 2007, the entire disclosure of which is hereby incorporated by reference.

Technical Field The present invention relates to a

Punching press according to the preamble of claim 1.

State of the art

In the industry, 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 Zugsäule, a maximum tilting stiffness both in the direction of passage and at right angles to achieve. As an example of such 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. In this punch press, 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.

In view of the ever-increasing demands with regard to production flexibility, punching frequency and punching precision, 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.

Presentation of the invention

It is therefore an object to provide a punch press available, which does not have the aforementioned disadvantages of the prior art, or at least partially avoids.

This object is achieved by the punch press according to claim 1.

Accordingly, 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. For the operation of the stamping press, 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. The term "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. Furthermore, 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.

In a preferred embodiment of the punch press, 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. Under inclination 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. By this configuration, the structural complexity for the realization of the ram guide can be reduced to a minimum and it is the use of very short tension columns possible, which is advantageous in view of an undesirable elongation of the same under load. ^'

In a further preferred embodiment of the stamping press, two mutually opposite tension columns are rigidly connected to one another via a connecting element, such as, for example, via a yoke. This results in the advantage that the force components of two tension columns can be combined and skewed force components can be compensated by the yoke. To drive the two pillars, for example, a central crank mechanism is sufficient. The connection is advantageously carried out in the region of the press ram facing away from the ends of the tension columns. However, depending on the configuration of the tension column guides and the coupling of the tension columns to the drive mechanism, it is also conceivable to produce the abovementioned connection in a region between the two ends of the respective tension columns. This embodiment is particularly advantageous if the 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.

In yet another preferred embodiment, 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.

It is in embodiments of the punch press, in which two opposite tension columns are rigidly connected to each other via a connecting element, preferably, when in each case the opposite transverse to the strip running direction of the press tension columns are connected to each other at their lower ends via a transverse yoke. This has the advantage that a modular press design is possible. By combining identical drive and guide units with rams and clamping tables of different lengths, it is possible to form stamping presses of various lengths from a few different components. In yet another preferred embodiment, 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. In yet another preferred embodiment of the stamping press, 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. Depending on the design, 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.

It is preferred that 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. As a result, an inventive punch press can be realized in a simple and cost-effective manner, in which all tension columns are forcibly synchronized.

It is also preferred that exactly one 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.

In the aforementioned embodiment with exactly one crankshaft, it is further preferred that the 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. Such a structure has the advantage that an arrangement of the crank pin at the longitudinal position of the tension columns is possible, so that any by bearing forces generated bending moments in the press structure are avoided in the longitudinal direction.

It is further advantageous that the 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.

Further, in the two aforementioned embodiments of the punch press, it is preferable that the

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. As a result, the rotational moment of inertia of the crankshaft can be kept relatively small, with good rotational rigidity at the same time.

It is also preferred that 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. As a result, a separate production of smaller components is possible and a variety of crankshafts can be formed from a few components (modularity), so that manufacturing and storage costs can be reduced.

Furthermore, in embodiments of the punch press whose drive mechanism has at least one crankshaft with one or more associated connecting rods, it is preferred if the 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.

If the eccentrics and eccentric bushes of the respective crankpins are locked in certain positions relative to one another with locking means, preferably with a locking bolt, for fixing a specific lifting height of the crankshaft, adjustment to specific, precisely defined values is possible in a simple manner. In the case of the aforementioned embodiment, if the 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. This design allows a simple design with easier unlockability and thus easier Umstellbarkeit the machine to other lifting heights.

In yet another preferred embodiment of the punch press, whose drive mechanism has at least one crankshaft with one or more associated connecting rods, 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. This results in the advantage that the crankshaft has a defined axial bearing, in contrast to the usual "flying" storage.

In yet another preferred embodiment of the stamping press, 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. As a result, the basic structure of the punch press can be built up from a number of smaller, modular components, which enables savings in storage and production costs.

In a first alternative preferred embodiment of the punch press whose drive mechanism has at least one crankshaft with one or more to ^¬ parent conrod, the crank shaft remote end of 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). In this case, 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. Further, 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".

In such stamping presses, it is preferred that 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 Änlenkpunkt can be transmitted to the structure, so that share a Bie ^¬ gebeanspruchung of the articulation point forming construction substantially avoided. This is particularly advantageous if the articulation point is formed by an adjustable support arrangement, for example by a threaded spindle with which the vertical position of the Anlenk- kungspunktes is adjustable. It is also preferred that 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.

It is also preferred in this embodiment of the punch press, that in each case a guide is provided, by means of which the crankshaft remote end of the respective connecting rod is guided vertically, such that its articulation point for the lever or the only in the vertical direction is movable. This results in a horizontal determination of this Anlenkpunk- tes, which simplifies the articulation of two mirror-inverted opposite levers on a common connecting rod.

Accordingly, it is preferred that the 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 gelbildlicher way are each assigned to a train column. This results in the advantage of a compact design and a zwangsssynchronen drive two Zugsäulen. In a second alternative preferred

Embodiment of the punch press, 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). In this case, 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".

It is preferred that 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.

It is also preferred that 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.

It is also preferred in this embodiment of the punch press, that in each case a guide is present, by means of which the 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. As a result, the articulation of two mirror-inverted, horizontally fixed lever on a common connecting rod is possible. Accordingly, it is preferred that the 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 Zugsäule are assigned. This results in the pre ^¬ part of a compact design and a zwangsssynchronen drive two Zugsäulen. It is in variants of the above two alternative preferred embodiments of the punch press, in which the crankshaft remote end of the respective connecting rod at two opposite, seen in the crankshaft longitudinal direction mirror-image lever is articulated, preferred that the tension columns, where the mirror image opposite lever in the area below their leadership, in particular They are rigidly connected by a yoke. This results in a stabilization of the tension columns with each other and it is an advantageous introduction of the driving forces in the tension columns on the yoke lent possible.

It is also in variants of the two aforementioned alternative preferred embodiments of the punch press, which have means for compensating a load-induced elongation of the tension columns, preferred that 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.

This results in the advantage that an adjustment of the ram position is possible, with advantage also during the punching operation.

For this purpose, advantageously, 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.

Alternatively, it is also preferred that 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.

Such solutions are tried and tested, cost-effective and safe, and also allow automated adjustment / adjustment of the articulation point via a controller.

It is also in variants of the two aforementioned alternative preferred embodiments of the punch press, which have means for compensating a load-related elongation of the tension columns and in which several levers for moving up and down the Zugsäulen len are present, 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. In particular, for stamping presses with four tension columns, which are each arranged in the outer corners of the press ram, this results in the possibility of optimal compensation caused by eccentric load uneven component deformations (eg elongations of the tension columns) in punching operation, since the plunger by a specifically different Adjusting the positions of the articulation points of the lever can be held under load parallel to the clamping plate.

BRIEF DESCRIPTION OF THE DRAWINGS Further preferred embodiments of the invention will become apparent from the dependent claims and from the following description with reference to the figures. Showing: 1 shows a cross section through a first punching press according to the invention along the line AA in FIG. 2;

FIG. 2 shows a longitudinal section along the line B-B in FIG. 1; FIG.

Fig. 3 is a plan view of the punch press of Figures 1 and 2 with the press ram removed;

4 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;

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;

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. and

8 shows a section along the line E-E in Fig. 6th

Ways to carry out the invention

The basic structure of a first stamping press according to the invention can be seen in FIGS. 1 to 4, which 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).

As can be seen, 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. Above the clamping plate 23, 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. The guides 3, the construction of which is explained in more detail elsewhere with reference to FIGS. 5a and 5b, are tilt-tolerant and essentially torque-free and represent the only guides 3 for the press ram 1. As can be seen, they are arranged in such a way that that the center of their axial extent in the longitudinal direction of the tension columns 2 is exactly in the ideal or middle strip plane X. The two a common machine housing

15, 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 ends of these levers 7 facing away from the press center are articulated with lugs 7a on spindle nuts 20, which can be displaced vertically with spindles 19 in order to adjust the respective articulation points. The drive of these spindles 19 is based on worm wheels 18, which each take over together with a bearing assembly 17, the storage of the respective spindle 19. In order to prevent co-rotation of the spindle nut 20 during rotational movement of the spindle 19, the spindle nut 20 has an anti-rotation in the lid 20a.

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.

In the lower, large connecting rod bores of the connecting rods 8 is seated a common crank pin 9, 10 of a crankshaft 9, 10, 29 of the drive mechanism, which is formed by an eccentric 10 and an eccentric bushing 9. By rotating the eccentric bush 9 relative to the eccentric 10, the resulting total eccentricity of the crank pin 9, 10 can be changed, which corresponds to a change in the stroke of the crankshafts 9, 10, 29 and thus also an altered stroke of the punch press. In the present case, 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 Hubwechseln. Then, the eccentric 10 can be rotated relative to the eccentric bushing 9, while the eccentric bushing 9 is temporarily secured against rotation with a bolt 25 which can be inserted with a latching piston 26. 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. On the other side of the punch press are the drive assemblies 27 such as brake, clutch ment and flywheel with the crankshaft 9, 10, 29 arranged.

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. As can be seen, 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. By a corresponding adjustment of the articulation points of the tabs 7a can be a possible misalignment of the plunger 1, which is caused by eccentric load of the press ram 1, inter alia, by different elongations of the tension columns 2 compensate. Further details of these means previously described for compensating a load-related elongation of the tension columns of the drive mechanism are shown in the left half of Fig. 4, which 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 As can be seen, 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. By the lid 52 on the one hand, the lubricating oil is fed and on the other hand, the adjusting nut 51 countered. Thus, the guide shoes 50 to the column 2 towards or away from this in said thread with the nut 51 are adjustable. This results in the advantage that you can readjust the game of these guides very easy again after many years of use. The basic construction of a second stamping press according to the invention can be seen in FIGS. 6 to 8, which 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. As in the stamping press according to the invention shown in FIGS. 1 to 4, 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. As in the embodiment described above, 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 Zugsäulen 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.

In the lower, large connecting rod bores of the connecting rod 16, lβa sits common for both con rods crank pin 9, 10 of the crankshaft 9, 10, 28 of the drive mechanism, which is formed by an eccentric 10 and an eccentric bushing 9. The structure and the bearing of the crankshaft 9, 10, 28 are identical to the first embodiment according to Figures 1 to 4 and therefore need not be described again here. Since the movements are at the ends of the lever 7, 7a turned by the housing-fixed eccentric shafts, so that the pull tabs 6 move upward when the pressure plates 18, 18a go down and vice versa, takes place in this embodiment of the inventive punch press system already a certain balance of the moving masses.

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.

8 shows a section through one half of the lever mechanism of one side of the punching press along the line EE in FIG. 6. As can be seen, the 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. In their middle, 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.

Claims

claims

1. stamping press with a clamping plate (23, 27) and with one of the upper side of the clamping plate (23, 27) opposite and against the clamping plate (23, 27) working press ram (1), which via Zugsäu ^¬ len (2) with a below the press belt (1) is guided exclusively on the tension columns (2), which are guided such that an inclination of the press ram (1) and the tension columns (2) under eccentric load by inclination of the tension columns (2) around in the region of the belt running plane (X) of the punch press extending tilt axes around is possible.

2. Punching press according to claim 1, wherein the tension columns (2) are guided exclusively in the region of the strip running plane (X) of the punch press, in particular in tilt-tolerant and in particular substantially torque-free guides.

3. Punching press according to one of the preceding claims, wherein in each case two mutually opposite tension columns (2), in particular in the region of their ends facing away from the press ram, are rigidly connected to one another via a connecting element (5).

4. Punching press according to one of the preceding claims, wherein the punch press has exactly four tension columns (2), which are each arranged in the region of the outer corners of the plunger (1).

5. Punching press according to claim 3 and claim 4, wherein each of the transverse to the strip running direction of the press opposite tension columns (2) at their lower ends via a yoke (5) are interconnected.

6. punch press according to one of the preceding claims, wherein the drive mechanism means (18, 19, 20, 34, 35, 36 and 8, 20, 21, 22, 23) to compensate for a load-induced elongation of the tension columns (2) up ^' , in particular for the individual compensation of a load-related elongation of each train column (2).

7. punching press according to one of the preceding

Claims, wherein the drive mechanism has at least one crankshaft (9, 10, 29 or 9, 10, 28) with one or more associated connecting rods (8, 16, 16a) for converting a rotary drive movement into an intermittent upward and downward movement the drive of the tension columns (2) of the press ram (1).

8. punching press according to claim 7, wherein the crankshaft (9, 10, 29 or 9, 10, 28) extends in the longitudinal direction of the punch press, and in particular, wherein exactly one longitudinally extending crankshaft (9, 10, 29 or 9, 10, 28) for driving all tension columns (2) is present.

9. punch press according to claim 8, wherein the crankshaft (9, 10, 29 or 9, 10, 28) is arranged centrally along the longitudinal axis of the punch press, such that with respect to the tension columns (2) results in a symmetrical arrangement.

10. Punching press according to claim 9, wherein the crankshaft (9, 10, 29 or 9, 10, 28) exactly two crank pin (9, 10), which in each case in the region of one end of the crankshaft (9, 10, 29 and 9, 10, 28) are arranged and at least on the side facing away from the respective shaft end of a crank pin (9, 10) associated, in particular designed as a rolling bearing radial bearing (30) of the crankshaft (9, 10, 29 and 9, 10, 28) are flanked.

11. punching press according to claim 10, wherein the crank pin (9, 10) respectively on both sides of a crank pin (9, 10) associated, in particular designed as a rolling bearing radial bearing (30, 33) of the crankshaft (9, 10, 29 9, 10, 28) are flanked.

12. Punching press according to one of claims 10 to 11, wherein the crankshaft (9, 10, 29 or 9, 10, 28) in the region between those radial bearings (30), each on the side facing away from the shaft end of the respective crank pin (9, 10) are arranged, designed as a hollow shaft.

13. Punching press according to one of claims 11 to 12, wherein the crankshaft (9, 10, 29 or 9, 10, 28) is constructed as a built shaft, such that the part formed as a hollow shaft (29 or 28) as of the crank pin (9, 10) is formed separate component (29 or 28).

14. Punching press according to one of claims 7 to 13, wherein the crankshaft (9, 10, 29 or 9, 10, 28) is designed such that the lifting height of its crank pin (9, 10) is adjustable and in particular, wherein the crankshaft (9, 10, 29 or 9, 10, 28) crank pin (9, 10), each formed by an eccentric (10) and an eccentric bushing (9) rotatably mounted thereon, such that by rotation the eccentric bush (9) on the eccentric (10) different lifting heights of the crankshaft (9, 10, 29 or 9, 10, 28) are adjustable.

15. punch press according to claim 14, wherein the eccentric (10) and eccentric bushings (9) of the respective crank pin (9, 10) in certain positions to each other with locking means (32), in particular with a locking pin (32), can be locked, laying down a certain lifting height of the crankshaft (9, 10, 29 or 9, 10, 28).

16. Punching press according to claim 12 and claim 15, wherein the locking means (32) via a central release mechanism (31) are releasable, which extends through the interior of the hollow shaft formed as part (29 or 28) of the crankshaft (9, 10, 29 or 9, 10, 28).

17. Punching press according to one of claims 7 to 16, wherein the crankshaft (9, 10, 29 or 9, 10, 28) in radial bearings (30, 33) is mounted and exactly one of the radial bearing (30, 33) of the crankshaft (9, 10, 29 or 9, 10, 28) is designed as a fixed bearing (33) for receiving the forces acting on the crankshaft (9, 10, 29 or 9, 10, 28) axial forces.

18. Punching press according to one of claims 7 to 17, wherein the crankshaft (9, 10, 29 or 9, 10, 28) in radial bearings (30, 33) is mounted, which are each associated with one of the crank pin (9, 10) , and wherein the one or more radial bearing (30, 33) associated with or assigned to a crank pin (9, 10) is or are mounted in a separate housing part (15, 15b), each having a central, the clamping plate (23, 27 ) supporting or forming housing part (15 a) connected, in particular screwed.

19. A punch press according to any one of claims 7 to 18, wherein the crank shaft remote end of each connecting rod (8, 16, 16 a) at a first end of at least one lever (7) is hinged, which at its second end directly or indirectly to the structure (15 , 15a, 15b) of the punch press, such that the lever (7) can be swung back and forth about its second end by rotating the crankshaft (9, 10, 29) through the connecting rod (8), the lever (7) is pivotally connected in at least one tension column (2) of the punch press in a region between its first and second ends such that the tension column (2) is moved up and down by swinging the lever (7) back and forth can.

20. Punching press according to claim 19, wherein the respective lever (7) at its second end via a tab (7 a) on the structure (15, 15 a, 15 b) of the punch press is articulated.

21. Punching press according to one of claims 19 to 20, wherein the respective lever (7) in one area between its first and its second end via a tab (6) with the tension column (2) is connected.

22. Punching press according to one of claims 19 to 21, wherein in each case a guide (21, 22) is present, by means of which the crankshaft remote end of the respective connecting rod (8) is guided vertically, such that its articulation point on the respective lever (7) - Finally, is movable in the vertical direction.

23. Punching press according to claim 22, wherein the crankshaft remote end of the respective connecting rod (8) in a common pivot point at the first ends of two opposite, seen in the crankshaft longitudinal direction mirror image lever (7) is hinged, which seen in crankshaft longitudinal direction in each case a mirror image in particular Zugsäule (2) are assigned.

24. Punching press according to one of claims 7 to 18, wherein the crankshaft remote end of each connecting rod

(16, 16a) is connected to a first end of at least one lever (7, 7a) which is articulated in a region between its first and its second end to the structure (15, 15a) of the punch press, such that the lever ( 7, 7a) can be swiveled back and forth about its articulation point by rotating the crankshaft (9, 10, 28) through the connecting rod (16, 16a), the lever (7, 7a) pivoting at its second end at least one tension column (2) of the punch press is connected, such that the tension column (2) can be moved up and down by pivoting the lever (7, 7a) back and forth.

25. Punching press according to claim 24, wherein the respective lever (7, 7a) in a region between its first and its second end, in particular by means of a bolt (8) is articulated directly on the structure (15, 15a) of the punch press.

26. Punching press according to one of claims 24 to 25, wherein the respective lever (7, 7 a) at its second end via a tab (6) with the tension column (2) is connected.

27. Punching press according to one of claims 24 to 26, wherein in each case a guide (17, 17 a) is present, by means of which the crankshaft remote end of the respective connecting rod (16, 16 a) is guided vertically, such that it is movable exclusively in the vertical direction , and wherein the crankshaft remote end of the respective connecting rod (16, 16a) via a tab (18, 18a) to the first end of the at least one lever (7, 7a) is connected.

28. Punching press according to claim 27, wherein the crankshaft remote end of the respective connecting rod (16, 16a) via separate tabs (18, 18a) at the first ends of two opposite, seen in the crankshaft longitudinal direction mirror image lever (7, 7a) is articulated, which, in particular in crankshaft longitudinal direction, are assigned in each case in a mirror-image manner to a tension column (2).

29. punching press according to claim 23 or

Claim 28, wherein the tension columns (2), which are associated with the mirror image opposing levers (7, 7a) are rigidly connected to each other in the area below their leadership, in particular via a yoke (5).

30. Punching press according to claim 6 and any one of claims 19 to 29, wherein the means (18, 19, 20, 34, 35, 36 or 8, 20, 21, 22, 23) for compensating a load-related elongation of the tension columns ( 2) are designed such that with them the particular vertical position of the articulation point of the respective lever (7 or 7, 7a) on the structure (15, 15a, 15b) of the punch press is adjustable, in particular during operation of the press.

31. Punching press according to claim 30, wherein the

Position of the articulation point of the respective lever (7) on the structure (15, 15a, 15b) of the punch press by means of a threaded spindle (19) is adjustable, in particular by means of a threaded spindle (19) driving servomotor (34, 35).

32. Punching press according to claim 30, wherein the position of the articulation point of the respective lever (7,

7a) on the structure (15, 15a) of the punch press by means of an eccentric (8) is adjustable, in particular by means of a servomotor, in particular with planetary gear (20, 21, 22, 23), rotatable eccentric (8).

33. Punching press according to one of claims 30 to 32, with a plurality of levers (7 or 7, 7 a), which are each associated with a tension column (2), for upward and downward movement of the respective tension column (2) by pivoting back and forth associated lever (7 or 7, 7a) around its articulation point, wherein the positions of the articulation points of the lever (7 or 7, 7a) in groups or independently adjustable.