EP1650015A1 - Press, punch press or forming apparatus - Google Patents

Abstract

The machine has a lever gear with a pair of connecting rods (37, 38) that are flexibly connected with a connection rod (35) at an eccentric shaft on one side and with pushing units by respective crank stilts (42, 43) on other side, where the pushing units have an adjusting unit (55). The stilts are flexibly held at an upper part (13) of a frame (11) in the area between the respective connecting rods and units by supporting rods (45, 46).

Description

The invention relates to a press, stamping or forming machine with a frame which comprises a frame top, a frame base and the frame upper part on the frame base supporting stand, wherein the frame base has a platen and the frame top receives a single rotationally driven eccentric shaft, which via a symmetrical to a vertical center axis of the frame formed lever mechanism and two slidably held on the frame top thrust units with a relative to the platen back and forth movable plunger is coupled, which is held by means of guide elements in the vertical direction displaceable on the frame.

By means of press, stamping or forming machines, a workpiece can be machined by mounting a lower tool on the clamping plate and an upper tool on the clamping plate facing front side of the plunger, which cooperate with each other during reciprocation of the plunger to the between the upper tool For example, to stamp, punch or reshape a workpiece positioned on the lower tool. The drive of the plunger is effected by means of an eccentric shaft, which is coupled via a rotatably mounted on the eccentric shaft connecting rod with the plunger. Pressing or stamping machines are known from EP 1 308 268 A1, in which the course of movement and speed of the plunger during a rotation of the eccentric shaft is similar to a sine curve or a cosine curve.

There are also pressing, punching and forming machines are known in which the coupling of the eccentric shaft with the plunger via a lever mechanism and at least one push unit, wherein the lever mechanism in many cases at least has a toggle. In such a construction, the movement and speed course of the plunger can be changed so that the plunger passes through its lower dead center relatively slowly. This has the advantage that within the residence time of the plunger in an area adjacent to the bottom dead center, the material of the workpiece has sufficient time to flow. Due to the relatively slow forming process, embossing and edge contours can be optimally shaped. This allows a high dimensional accuracy of the workpieces. In addition, this vibration is reduced because the upper tool touches the workpiece at low speed. This results in longer tool life and better punching results.

From EP 1 223 027 A2 a press of the type mentioned is known in which the lever mechanism has two pairs of slides, which are mounted to each other displaceable in a vertical distance on the frame top. The slides are coupled via articulated levers, which in turn are articulated to a toggle. Overall, the known press is characterized by a complex construction.

Object of the present invention is to develop a pressing, punching or forming machines of the type mentioned in such a way that it has a structurally simpler design with the least possible influence of lateral force on the pressing, punching or forming tool.

This object is achieved in a pressing, punching or forming machines of the generic type according to the invention that the lever mechanism has a pair of push rods, on the one hand with a on the eccentric shaft rotatably mounted connecting rods and on the other hand in each case via a first Kurbelstelze with a thrust unit are articulated, wherein the first Kurbelstelzen are held in the region between the respective push rod and the thrust unit via a first support strut articulated on the frame top.

The conversion of the rotational movement of the eccentric shaft in a reciprocating motion of the plunger takes place in the pressing, stamping or forming machines according to the invention via a rotatably mounted on the eccentric shaft connecting rod, at the end remote from the eccentric shaft two push rods are articulated with their the connecting rod opposite end are each hingedly connected to a, first Kurbelstelze, which in turn is articulated to a push unit. The first Kurbelstelze is additionally held articulated on the frame top, this is articulated in the region between the push rod and the thrust unit to the first Kurbelstelze a first support strut, which is pivotally connected at its end facing away from the first Kurbelstelze end with the frame top. Moves the connecting rod due to the rotational movement of the eccentric shaft down, that is in the direction of the platen, the two hinged to the connecting rod push rods are spread apart, so that the pivot points, where the push rods are each connected to a first Kurbelstelze, the Approach articulation points at which the first support struts are articulated on the frame top. This in turn has the consequence that the first crank stilts also move with their end portions facing away from the respective push rod down in the direction of the platen and thereby exert a pushing force on the thrust units, so that the plunger is moved in the direction of platen. Moves the connecting rod in the further rotational movement of the eccentric shaft back up, that is, in the direction of the platen facing away, so pivot the two push rods towards each other, and this has the consequence that the points of articulation, at which the first push rods are connected to the Kurbelstelzen, remove from the articulation points, where the first support struts are connected to the Gestelobererteil, and this in turn causes the first crank stilts perform an upward movement with their end region facing away from the push rod, so that the push rod is moved upwards via the push units. Thus, by rotation of the eccentric shaft in a structurally simple manner, a reciprocating motion of the plunger can be generated.

The power flow is in the construction according to the invention of the push rods directly on the first Kurbelstelzen over. This allows a higher force application and causes a higher rigidity of the system. The crank stilts are supported via the support struts directly on the frame top. This has the consequence that the opposing force acting on the plunger during pressing, stamping or forming can be introduced directly into the frame upper part from the crank stilts via the support struts. A higher tilting stiffness is also achieved in that not only the plunger is held displaceably on the frame by means of the guide elements, but also in addition the thrust units, via which the plunger is driven to reciprocate relative to the platen, slidably mounted on the frame top are. Lateral forces caused by the lever mechanism are thus introduced into the frame upper part, so that on the drive side the ram is acted on only with a vertically oriented driving force, while horizontal forces are absorbed by the frame upper part. Also off-center on the ram attacking forming forces can be transmitted via the sliding bearing of the thrust units on the frame top. The danger of unintentional Displacement or tilting of the plunger is thereby reduced, so that the required to achieve highly precise workpieces and long tool life parallelism between the end face of the plunger and the top of the platen is guaranteed. Due to the use of the lever mechanism, the plunger has a relatively long residence time in the region of its bottom dead center, so that the workpiece is subjected to a relatively slow forming process.

The stroke of the plunger, that is, the distance between its top and bottom dead center, in the pressing, stamping or forming machines according to the invention in the usual manner by means of a double eccentric, as is known in the art, be changed.

But the stroke of the plunger can also be influenced by changing the length of the two push rods. It has been shown that a shortening of the push rods and thus an increase in the distance of the articulation points at which the first crank stilts are connected to the push rods and the first support struts with the frame top, an increase in the stroke result. Conversely, the stroke can be shortened by reducing the distance of said articulation points by extending the push rods. It is particularly advantageous, therefore, if the push rods are formed variable in length.

In an advantageous embodiment, the first support struts are articulated in the longitudinal direction of the respective first Kurbelstelze centrally to the first Kurbelstelze. The first crank stilts are thus held in the longitudinal direction centrally in each case via a first support strut articulated on the frame top. The first The crank handle forms a double-armed lever which can be pivoted about the central articulation point and whose lever arms are of equal length. Acting leverage forces are transmitted in a ratio of 1: 1.

It is advantageous if the first crank stilts are twice as long as the first support struts.

It can be provided that the axis of rotation of the eccentric shaft crosses the central axis of the frame perpendicularly. The eccentric shaft is arranged in such a configuration on the central axis. This has the consequence that the path and speed course of the plunger is symmetrical to its bottom dead center. Under the course of the path covered by the plunger, that is, the respectively assumed plunger position, understood in dependence on the rotation angle of the eccentric shaft; the speed profile is understood to mean the speed of the tappet as a function of the angle of rotation of the eccentric shaft. In an arrangement of the eccentric shaft on the central axis of the frame, the course of the amount of the speed of the plunger during a downward movement corresponds to the course of the amount of speed in an upward movement of the plunger.

But can also be provided particularly advantageous that the axis of rotation of the eccentric shaft is arranged offset from the central axis of the frame. This has the consequence that the path and speed course of the plunger is asymmetrical with respect to its bottom dead center. The course of the speed of the plunger in its downward movement thus does not correspond to the course of the speed in its upward movement. In particular, by an offset to the central axis of the frame arrangement of the axis of rotation of the eccentric shaft a speed profile of the plunger are achieved, in which it approaches its lower dead center at relatively low speed, passes through it and then performs an upward movement at high speed.

It is particularly advantageous if the position of the eccentric shaft relative to the central axis of the frame is variable, because thereby the speed profile of the plunger can be optimally adapted to the respective manufacturing process. For example, the eccentric shaft can be rotatably mounted on at least one carriage slidably held on the frame upper part, so that the axis of rotation of the eccentric shaft can be displaced relative to the center axis of the frame by displacing the carriage. The drive of the carriage can be effected by means of a motor, preferably by means of an electronic servo or hydraulic motor.

The thrust units of the pressing, punching or forming machines according to the invention are held by means of guide devices displaceable on the frame top. In order to relieve the guide means of shear forces, in an advantageous embodiment, the connecting rod and the two push rods are articulated to a slide which is held coaxially to the central axis slidably on the frame top.

A transverse force introduction into the plunger can advantageously also be reduced in that the lower end regions of the first crank stilts are connected to one another via a crossbar.

It is particularly advantageous if the connecting rod are articulated to a first articulation point and the two push rods at a second articulation point to the slider, wherein the distance between the two articulation points is variable. A change in the distance between the two articulation points has a change in the stroke of the plunger result, that is, by changing the distance of the articulation points, the distance between the upper and lower dead center of the plunger can be adjusted. This has the advantage that the eccentric shaft can be configured with a fixed stroke.

A change in the distance of the articulation points can be achieved in a structurally simple manner in that the slide comprises a spindle, with which the connecting rod and the two push rods are articulated at a distance from each other. The spindle may comprise a first threaded portion with a right-hand thread and a second threaded portion with a left-hand thread, the threaded portions each being in engagement with a support nut to which the connecting rod or the two push rods are articulated. By rotation of the spindle can thus be changed in a structurally simple manner, the distance of the articulation points for adjusting the stroke of the plunger. For the rotary drive of the spindle, a servomotor can be used.

A stroke adjustment is achieved in a particularly preferred embodiment of the invention in that the first support struts are held in the vertical direction adjustable articulated on the frame top. The pivot point at which the support struts are pivotally connected to the Gestelloberteil can thus be raised and lowered, and this has the consequence that the stroke, which performs the plunger in its reciprocating movement changed becomes. The eccentric shaft can consequently be designed as a pure Festhubwelle, the use of double eccentric stroke adjustment of the plunger can be omitted.

The adjustable mounting of the first support struts can be achieved, for example, in that the first support struts are each connected in an articulated manner to a spindle mounted on the frame upper part. It can be provided that the spindle is in engagement with a support nut, to which a first support strut is articulated, wherein the spindle about its longitudinal axis in rotation is displaceable for raising and lowering the support nut and thus the articulated mounting of the first support strut. For rotary drive of the spindle, a servo motor may be provided.

During the reciprocation of the plunger, high mass forces occur. To compensate for these inertial forces, in a particularly preferred embodiment above the eccentric shaft arranged by means of guide elements in the vertical direction displaceable on the frame top balancing mass arranged, wherein the two push rods are each connected via a second Kurbelstelze articulated to the balancing mass. Such a configuration allows in a structurally simple manner a phase-shifted by 180 ° back and forth movement of the balancing mass relative to the reciprocating motion of the plunger.

It is advantageous here if the first and second Kurbelstelzen are the same length. The two Kurbelstelzen thus form a toggle lever, which can be stretched periodically by means of the respective push rod, which is pivotally connected to the connecting rod.

It is advantageous if a first and a second Kurbelstelze are hingedly connected to a common pivot point with a push rod. This has the consequence that the push rod transmits equal mass forces to the articulated crank stilts.

It is particularly advantageous if the second Kurbelstelzen are held in the region between the respective push rod and the balancing mass via a second support strut articulated on the frame top. This gives the lever mechanism a particularly high mechanical strength.

Preferably, the second support struts are articulated centrally in the longitudinal direction of the respective second Kurbelstelze to the second Kurbelstelze. The second Kurbelstelze thus forms a two-armed lever which is pivotally supported about the articulation point of the second support strut and comprises two equal length lever arms.

It is favorable if the second crank stilts are twice as long as the second support struts.

In a particularly preferred embodiment, the second support struts are the same length as the first support struts.

It is advantageous if in each case a first and a second support strut at a common pivot point are pivotally connected to the frame top. The two support struts can in this case be held on a common bolt, which is rotatably mounted on the frame top.

With common storage of a first and a second support strut on the frame upper part may be provided for adjusting the stroke of the plunger, that the first and second support struts are held in the vertical direction together adjustable on the frame top articulated. As already explained above in connection with the first support strut, the stroke of the plunger can be adjusted in a structurally simple manner by raising and lowering the pivot point on which the support struts are pivotally connected to the frame top.

With regard to the guide elements, with the help of the plunger and the balancing mass are slidably held on the frame, no details have been made so far. It can be provided, for example, that the plunger and / or the leveling compound are held displaceably by means of guide columns and associated guide bearings.

It is advantageous if the guide columns are fixed to the plunger and the guide bearings are held on the frame. It can be used in each case four with the ram follower guide columns, which are guided in rolling or sliding guides. The sliding guides can be hydrodynamically or hydrostatically lubricated. Both flat guides and round guides can be used. The balancing mass associated guide columns can be fixed to the balancing mass or on the frame, with four stationary or follower guide columns can be used. Preferably, the guide columns of the balancing mass are fixed to the frame and the associated guide bearings are arranged on the balancing mass.

A particularly tilt-resistant ram guide can be achieved in that the guide columns fixed to the ram are mounted displaceably above and below a strip running plane by means of a sliding or rolling element guide. The guide columns can each be displaceably mounted below the strip running plane by means of a first guide bush, preferably a sliding or rolling guide, above the strip running plane and by means of a second guide bush, preferably a sliding or rolling guide. When using four guide columns thus results in an 8-fold storage of the plunger on the frame, and in addition, the two thrust units are slidably mounted on the frame. The 8-fold storage by means of rolling guides has the advantage that the guide columns can be performed without play, both above and below the strip running plane in prestressed rolling elements. Here, the distance between the rolling guides of a guide column can be a multiple of the maximum stroke of the plunger.

In a particularly preferred embodiment, the thrust units comprise an adjusting device for adjusting the position of the bottom dead center of the plunger during operation of the press or of the stamping or forming machine. The quality of the machined workpieces as well as the tool life depends on the position of the bottom dead center of the plunger. In particular, during acceleration phases and due to temperature changes, the position of the bottom dead center of the plunger can change, and to counteract such a change during operation of the pressing, stamping or forming machines, the adjustment is used, with the help of the effective length of the Thrust units can be changed.

The adjusting device is preferably arranged on the frame, that is on a stationary component. As a result, the service life of the press, punching or forming machine can be extended and its reliability and process reliability can be increased.

The adjustment of the position of the bottom dead center of the plunger can be achieved in a structurally simple manner, characterized in that the thrust units each having two mutually cooperating thrust arms, which are mutually displaceable by means of the adjusting device in the vertical direction. The thrust units can be designed telescopically in such an embodiment by one of the two push arms dips into a receptacle of the other push arm and relative to the other push arm is displaceable by means of the adjusting device.

It can be provided, for example, that the two push arms are connected to one another via a thread, wherein at least one end region of a push arm by means of the adjusting device is rotatable relative to the other push arm about the threaded axis.

Figur 1:

eine schematische Darstellung einer ersten Ausführungsform eines erfindungsgemäßen Press- , Stanz- oder Umformautomaten;

Figur 2:

eine schematische Darstellung einer zweiten Ausführungsform eines erfindungsgemäßen Press-, Stanz- oder Umformautomaten;

Figur 3:

eine schematische Darstellung der Wegverläufe der Stößel der Press-, Stanz- oder Umformautomaten gemäß der Figuren 1 und 2;

Figur 4:

eine schematische Darstellung der Geschwindigkeitsver-läufe der Stößel der Press-, Stanz- oder Umformautomaten gemäß der Figuren 1 und 2;

Figur 5 - Figur 15:

schematische Darstellungen dritter bis dreizehnter Ausführungsformen erfindungsgemäßer Press-, Stanz- oder Umformautomaten.

The following description of preferred embodiments of the invention is used in conjunction with the drawings for further explanation. Show it:

FIG. 1:

a schematic representation of a first embodiment of a pressing, stamping or forming machines according to the invention;

FIG. 2:

a schematic representation of a second embodiment of a pressing, stamping or forming machines according to the invention;

FIG. 3:

a schematic representation of the path profiles of the ram of the pressing, stamping or forming machines according to Figures 1 and 2;

FIG. 4:

a schematic representation of the speed of the tappets of the stamping, stamping or forming machines according to Figures 1 and 2;

FIG. 5 - FIG. 15:

schematic representations of third to thirteenth embodiments of inventive press, stamping or forming machines.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 schematically shows a first embodiment of a stamping, stamping or forming machine, which is generally designated by the reference numeral 10 and has a frame-like frame 11 which has a frame bottom part 12 and a frame top part 13. The frame top 13 is supported by means of four arranged at the corners of a rectangle stand 14 on the frame base 12.

At Gestelloberteil 13 an eccentric shaft 16 is rotatably supported by rolling or sliding bearing, which is rotationally driven by a known per se and therefore not shown in the drawing drive motor. The eccentric shaft 16 serves to drive a plunger 18, on each of which a stator 14th adjacent a total of four guide columns 19 are fixed, which are mounted by means of a first rolling guide 20 on the frame top 13 and by means of a second rolling guide 21 on the frame base in the vertical direction slidably. The first rolling guides 20 are above a belt running plane 23 and the second rolling guides 21 are positioned below the belt running plane 23. The strip running plane 23 forms the plane within which workpieces to be processed are positioned during operation of the press, stamping or forming machine 10.

The plunger 18 has an end face 25, which faces a platen 26 of the frame base 12. On the front side 25 upper tools and on the platen 26 associated lower tools can be mounted for machining the workpieces in the strip running plane 23rd

The coupling of the plunger 18 with the eccentric shaft 16 via a lever mechanism 29 which is symmetrical to a vertical center axis 30 of the pressing, punching or forming machines 10, and two of the lever mechanism 29 downstream and identically designed thrust units 32, 33rd Das Lever 29 is connected via a rotatably mounted on the eccentric shaft 16 connecting rod 35 with the eccentric shaft 16 and has two obliquely aligned push rods 37, 38 which are hinged at a common pivot point to the eccentric shaft 16 remote from the end of the connecting rod 35 by means of a Bolzens, which engages in the illustrated embodiment, a coaxially to the central axis 30 slidably mounted on the frame top 13 slider 40. However, the use of the slider 40 is absolutely necessary neither in the first embodiment nor in the other embodiments explained below. At the slide 40 and the Connecting rod 35 facing away from the end of the push rods 37, 38 is respectively a first Kurbelstelze 42 and 43 hinged, which is held in the longitudinal direction centrally by means of a first support strut 45 and 46 hinged to the frame top 13. At the respective push rod 37 and 38 facing away from the end of the crank stilts 42, 43 each have a push unit 32 and 33 articulated.

The thrust units 32, 33 each have an upper thrust arm 48 and a lower thrust arm 49, which are adjustably coupled to each other via a thread 50 in the vertical direction. The upper push arm 48 is slidably held in a guide means 52 of the Gestelloberteils 13 parallel to the central axis 30, and the lower push arm 49 is connected with its upper thrust arm 48 remote from the end with a pressure plate 53 which is rotatably supported about a vertical axis of rotation on the plunger 18 ,

The lower thrust arm 49 carries at its upper end portion facing the upper thrust arm 48 a sleeve 56 rotatable about the axis of the thread 50 by means of an adjusting device 55, into which the upper thrust arm 48 is screwed with its lower end portion. By means of the adjusting device 55, the sleeve 56 can be rotated, thereby changing the effective length of the respective thrust unit 32, 33 and thereby adjust the position of the bottom dead center tappet 18 during operation of the pressing, punching or forming machines 10.

As already explained, the crank stilts 42, 43 are each articulated via a first support strut 45 or 46 on the frame upper part 13. The first support struts 45, 46 are facing away with their respective Kurbelstelze 42 and 43, respectively End pivotally mounted in a stationary bearing 58 and 59 of the Gestelloberteils 13.

The rotational movement of the eccentric shaft 16 is transmitted by means of the connecting rod 35, the lever mechanism 29 and the thrust units 32, 33 in a reciprocating motion of the plunger 18. If the connecting rod 35 is moved downward by the eccentric shaft 16, that is to say in the direction of the clamping plate 26, the two push rods 37, 38 articulated on the connecting rod 35 and the slider 40 move apart and the crank stilts 42 articulated to the push rods 37, 38 pivot, 43 lead in the form of double-armed lever, which are mounted centrally pivotally in the longitudinal direction of the respective support strut 45 and 46, a tilting movement, so that the thrust units 32, 33 move in the direction of platen 26. The displaceable mounting of the connecting rod 35 and the push rods 37, 38 on the frame upper part 13 by means of the slider 40 relieves the thrust units 32, 33 and thus also the plunger 18 of transverse forces.

A relief of the plunger 18 of lateral forces can also be achieved by a dashed line shown in Figure 1 crossbar 61, which connects the lower, that is the plunger 18 facing ends of the first crank stilts 42, 43 together. Such a crossbar 61 forms a coupling member which directly couples the first crank stems 42, 43 and is oriented perpendicularly to the central axis 30 and which can be used in all of the embodiments explained below.

2 shows schematically a second embodiment of a pressing, punching or forming machine according to the invention is shown, which is generally designated by the reference numeral 70. The pressing, punching or forming machine 70 is similar to the press, punching or forming 10. As in the embodiments explained below and shown in Figures 5 to 15 are therefore identical components in Figure 2 denoted by the same reference numerals as in Figure 1 and with respect to these components to avoid repetition, reference is made to the above explanations.

From the first embodiment shown in Figure 1, the second embodiment shown in Figure 2 differs in that the eccentric shaft 16 is arranged offset to the central axis 30. The offset to the central axis 30 arrangement of the eccentric shaft 16 has the consequence that the plunger 18 has a relation to the bottom dead center asymmetric velocity course by approaching the bottom dead center in a downward movement at a slower speed and after passing through the bottom dead center compared with the first Embodiment performs a faster upward movement. The qualitative path and speed profile of the plunger 18 in the first embodiment shown in Figure 1 and the second embodiment shown in Figure 2 can be seen from Figures 3 and 4. FIG. 3 schematically shows the profile of the normalized plunger position as a function of the crank angle, that is to say the angle of rotation of the eccentric shaft 16. By definition, a crank angle of 180 ° corresponds to the bottom dead center of the plunger 18. The curve shown by the reference numeral 73 shows the travel of the plunger 18 the first embodiment shown in Figure 1. This path is symmetrical to the bottom dead center, that is, the crank angle of 180 °. In contrast to this, the curve which is identified by the reference numeral 74 and which represents the travel of the plunger 18 of the second embodiment with an eccentric shaft 16 offset from the central axis 30, an unbalance with respect to the bottom dead center such that the plunger 18 of the second embodiment approaches the bottom dead center earlier than the plunger 18 of the first embodiment and thus spends an overall longer period in the area of bottom dead center. This is also clear from FIG. 4, which schematically reproduces the qualitative velocity profile of the tappets 18 of the first and second embodiments. Reference numeral 76 denotes the curve representing the velocity pattern of the plunger 18 of the first embodiment, and reference numeral 77 denotes the curve illustrating the velocity pattern of the plunger 18 of the second embodiment. It is clear that the offset to the central axis 30 arrangement of the eccentric shaft 16 has a relation to the bottom dead center (crank angle 180 °) unbalanced velocity course of the plunger 18 result in this by its upward movement, that is, after passing through the bottom dead center, a considerable higher speed than the plunger 18 of the first embodiment. By shifting the eccentric shaft 16 relative to the central axis 30, a speed and path profile of the plunger 18, which is optimal for machining a workpiece, can thus be generated in order to give the material of the workpiece sufficient time to flow during its machining, so that relatively slow forming processes can be achieved high dimensional accuracy can be performed.

In FIG. 5, a third embodiment of a pressing, stamping or forming machine according to the invention is illustrated schematically and is designated by the reference numeral 80. Of the second embodiment shown in Figure 2, the pressing, stamping or forming machine 80 differs in that the first support struts 45, 46 not by means of a fixed bearing mounted on the frame top 13, the storage of the first support struts 45 and 46 on the frame top 13 takes place in the third embodiment shown in Figure 5 rather by means of an adjustment 81 and 82, with the aid of the articulation points 83, 84 of the first support struts 45 and 46th can be adjusted in the vertical direction on the frame top 13. The adjusting mechanisms 81, 82 are identical and each comprise a rotatable about its longitudinal axis spindle 86, with which a support nut is engaged, to which the first support strut 45 and 46 is articulated. By turning the spindle 86, the support nut and thus also the articulation point 83 and 84 of the first support strut 45 and 46 can be adjusted in the vertical direction. The rotary drive of the spindle 86 by means of at least one not shown in the drawing, known in the art engine, which may be preferably an electric servo or a hydraulic motor.

The raising and lowering of the articulation points 83, 84 of the first support struts 45 and 46 has the consequence that the stroke of the plunger 18 changes. The stroke can be increased and decreased by means of adjusting mechanisms 81, 82 during operation of the pressing, punching or forming machines 80. Under the stroke of the plunger 18 in this case the difference in the position of the end face 25 of the plunger 18 at its top dead center and understood his bottom dead center. The third embodiment shown in Figure 5 thus makes it possible to change during operation both the position of the bottom dead center of the plunger 18 and its stroke. For this purpose, on the one hand the adjusting devices 55 and on the other the adjusting mechanisms 81, 82 are used.

FIG. 6 schematically shows a fourth embodiment of a pressing, punching or forming machine according to the invention, which is designated overall by the reference numeral 90. It differs from the first embodiment shown in Figure 1 in that the frame upper part 13 above the eccentric shaft 16, an oscillating balance mass 91 is arranged to compensate for the mass forces occurring during the movement of the plunger 18. On the balancing mass 91, four guide columns 92 are fixed, which are each arranged parallel to a guide column 19 of the plunger 18 and are slidably mounted by means of an upper Wälzführung 93 and a lower roller guide 94 on the frame upper part 13. However, such a definition and storage of the guide columns is not mandatory. It may also be provided to fix the guide columns 92 on the frame upper part 13 and to arrange the roller guides 93, 94 on the balancing mass 91.

The balancing mass 91 is connected via two second crank stilts 96, 97 pivotally connected to the push rods 37 and 38 respectively. For this purpose, the second Kurbelstelzen 96, 97 are each articulated at a pivot point 98 and 99 together with a first Kurbelstelze 42 and 43 to the push rod 37 and 38 respectively. By rotation of the eccentric shaft 16 and the movement of the push rods 37, 38 generated via the connecting rod 35, the associated first and second Kurbelstelzen 42, 96 and 43, 97 are pivoted apart, so that the balancing mass 91 based on the movement of the plunger 18 performs 180 ° phase-shifted reciprocating motion, that is, in a downward movement of the plunger 18, the balancing mass 91 is moved upward and during an upward movement of the plunger 18, the balancing mass 91 performs a downward movement.

Even with the use of a balancing mass 91, an asymmetrical path and speed course of the ram 18 and thus also of the balancing mass 91 can be generated by an offset to the central axis 30 arrangement of the eccentric shaft 16. FIG. 7 shows schematically a fifth embodiment of a pressing, punching or forming automatic machine according to the invention, which is different from the fourth embodiment shown in FIG. 6 only by an arrangement of the eccentric shaft 16 with respect to the central axis 30.

FIG. 8 schematically shows a sixth embodiment of a pressing, punching or forming machine according to the invention, which is generally designated by the reference numeral 110 and which is configured similarly to the third embodiment illustrated in FIG. Also in the pressing, stamping or forming machines 110 can be changed by means of adjusting mechanisms 81, 82, the stroke of the plunger 18 during operation, wherein in the sixth embodiment according to the embodiments shown in Figures 6 and 7 in addition a balancing mass 91 is used to compensate for inertial forces.

FIG. 9 shows a seventh embodiment of a pressing, punching or forming machine according to the invention which is designated overall by the reference numeral 120. This also has adjusting mechanisms 81, 82 for stroke adjustment of the plunger 18 and a balancing mass 91. From the illustrated in Figure 8 sixth embodiment, the pressing, stamping or forming machine 120 differs only by the positioning of the eccentric shaft 16 on the central axis 30. Der Path and speed course of the ram 18 of the seventh embodiment is thus symmetrical to its bottom dead center, as has already been explained above with reference to Figures 1, 3 and 4 in detail.

FIG. 10 shows an eighth embodiment of a pressing, stamping or forming automatic machine according to the invention, in which a balancing mass 91 is likewise provided and displaces the eccentric shaft 16 in accordance with the fifth and sixth embodiments illustrated in FIGS. 7 and 8 is arranged to the central axis 30. In contrast to the fifth and sixth embodiments 100 and 110, however, in the eighth embodiment 130 shown in FIG. 10, an adjustment mechanism 131 arranged in the slide 40 is used, while the bearing of the first support struts 45, 46 on the frame top 13 by means of stationary bearings 58, 59 takes place. About the adjusting mechanism 131, the connecting rod 35 and the push rods 37, 38 are coupled together. The connecting rod 35 is pivotally connected at an upper pivot point 132 with the adjustment mechanism 131 and the two push rods 37 and 38 are pivotally connected together at a lower pivot point 133 to the adjustment mechanism 131. By means of the adjustment mechanism 131, the vertical distance, the two pivot points 132 and 133 occupy each other, are adjusted, thereby changing the stroke of the plunger 18. The adjusting mechanism 131 has for this purpose a coaxially aligned to the central axis 30 spindle 134 which can be rotated about its longitudinal axis by means of a servo motor, not shown in the drawing and which carries in its one end a right-hand thread and in its other end a left-hand thread, said These areas of the spindle are each in engagement with a support nut, on which the connecting rod 35 and the push rods 37, 38th are articulated. By rotation of the spindle 134 can thus be adjusted to each other in a structurally simple manner during operation of the pressing, stamping or forming machines 130, the distance between the pivot points 132, 133.

FIG. 11 shows a ninth embodiment of a press, punching or forming machine according to the invention, which is generally denoted by the reference numeral 140 and which is designed substantially identical to the fourth embodiment illustrated in FIG. However, no slider 40 is slidably mounted in the vertical direction on the frame top 13, such a slider 40 is omitted rather in the ninth embodiment. The second Kurbelstelzen 96 and 97 are supported in press stamping or forming 140 each by means of a second support strut 141 and 142 articulated on the frame upper part 13. Such second support struts 141, 142 may optionally also be used in all the above-described embodiments which have a balancing mass 91. The second support struts 141, 142 are hinged in the longitudinal direction of the respective second Kurbelstelze 96 and 97 centrally to the Kurbelstelze 96 and 97 and facing away from the respective Kurbelstelze 96, 97 end in each case together with a first support strut 45 and 46 on the stationary bearing 58 and 59 held pivotally.

Without the slider 40 is used, the eccentric shaft 16 can be arranged offset to the central axis 30 even when using the second support struts 141, 142. Such a configuration shows the illustrated in Figure 12 tenth embodiment of a pressing, stamping or forming machine according to the invention, which is generally designated by the reference numeral 150.

The use of the second support struts 141, 142 does not exclude the additional use of a slider 40, which is mounted coaxially to the central axis 30 slidably on the frame top 13, but such a slider 40 can be used in addition to the second support struts 141, 142. This is illustrated in FIG. 13, which schematically reproduces an eleventh embodiment of a pressing, punching or forming machine according to the invention, which is denoted overall by the reference numeral 160. The use of the slider 40 in addition to the second support struts 141, 142 has a particularly high tilting rigidity of the plunger 18 result.

In FIG. 14, a twelfth embodiment of a pressing, punching or forming machine according to the invention, indicated overall by the reference numeral 170, is schematically illustrated, which differs from the eleventh embodiment illustrated in FIG. 13 by an arrangement of the eccentric shaft 16 offset from the central axis 30. As already explained, by means of such a positioning of the eccentric shaft 16, it is possible to generate a path and speed profile of the plunger 18 which is asymmetrical relative to the bottom dead center.

Finally, FIG. 15 schematically shows a thirteenth embodiment of a pressing, punching or forming machine according to the invention, in which the second crank stems 96, 97 are articulated on the frame upper part 13 by means of second support struts 141, 142 and additionally a slide 40 is used. In a similar manner as in the eighth embodiment illustrated in FIG. 10, the slide 40 receives an adjustment mechanism 131, so that the stroke of the Plunger 18 can be adjusted during operation of the press, punching or forming machine 180 by the mutual distance of the articulation points 131 and 132 of the connecting rod 35 and the push rods 37, 38 is changed.

Claims (26)

Pressing, stamping or forming machine with a frame (11) comprising a frame top (13), a frame base (12) and the frame top (13) on the frame base (12) supporting stand (14), wherein the frame base (12) a clamping plate (26) and the frame upper part (13) a single rotationally driven eccentric shaft (16) receives, via a symmetrically to a vertical central axis (30) of the frame (11) formed lever mechanism (29) and two on the Gestelloberteil (13) slidable thrust units (32, 33) is coupled to a relative to the platen (26) reciprocable plunger (18) which is held by means of guide elements (19, 20, 21) displaceable in the vertical direction on the frame (11), characterized in that the lever mechanism (29) comprises a pair of push rods (37, 38), on the one hand with a rotatably mounted on the eccentric shaft (16) connecting rod (35) and on the other hand via a first Kurbelstelze (42, 43) a thrust unit (32, 33) are articulated, wherein the first Kurbelstelzen (42, 43) in the region between the respective push rod (37, 38) and the thrust unit (32, 33) via a first support strut (45, 46) hinged on Gestelloberteil (13) are held. Press-stamping or forming machine according to claim 1, characterized in that the push rods are variable in length. Pressing, stamping or forming machine according to claim 1 or 2, characterized in that the first support struts (45, 46) in the longitudinal direction the respective first Kurbelstelze (42, 43) are hinged in the middle of the first Kurbelstelze (42, 43). Pressing, stamping or forming machine according to claim 1, 2 or 3, characterized in that the first Kurbelstelzen (42, 43) are twice as long as the first support struts (45, 46). Pressing, stamping or forming machine according to claim 1, 2, 3 or 4, characterized in that the axis of rotation of the eccentric shaft (16) perpendicularly crosses the central axis (30) of the frame (11). Pressing, stamping or forming machine according to claim 1, 2, 3 or 4, characterized in that the axis of rotation of the eccentric shaft (16) to the central axis (30) of the frame (11) is arranged offset. Pressing, stamping or forming machine according to one of the preceding claims, characterized in that the connecting rod (35) and the two push rods (37, 38) are articulated to a slide (40), the coaxial with the central axis (30) displaceable on the frame top (13) is held. Pressing, stamping or forming machine according to claim 7, characterized in that the connecting rod (35) at a first pivot point (132) and the two push rods (37, 38) at a second pivot point (133) articulated to the slider (40) are, wherein the distance between the two articulation points (132, 133) is variable. Pressing, stamping or forming machine according to claim 8, characterized in that the slide (40) comprises a spindle (134), with which the connecting rod (35) and the two push rods (37, 38) are articulated at a distance from each other. Pressing, punching or forming machine according to one of the preceding claims, characterized in that the first support struts (45, 46) are held in the vertical direction adjustable on the frame top part (13) articulated. Pressing, punching or forming machine according to claim 10, characterized in that the first support struts (45, 46) are each pivotally connected to a spindle (86) mounted on the frame upper part (13). Pressing, stamping or forming machine according to one of the preceding claims, characterized in that above the eccentric shaft (16) by means of guide elements (92, 93, 94) displaceable in the vertical direction on the upper frame part (13) held balancing mass (91) is arranged, wherein the two push rods (37, 38) in each case via a second Kurbelstelze (96, 97) are pivotally connected to the balancing mass (91). Pressing, stamping or forming machine according to claim 12, characterized in that the first and second Kurbelstelzen (42, 43, 96, 97) are of equal length. Pressing, stamping or forming machine according to claim 12 or 13, characterized in that a first and a second Kurbelstelze (42, 43, 96, 97) at a common pivot point (98; 99) with a push rod (37, 38) hinged are connected. Pressing, stamping or forming machine according to claim 12, 13 or 14, characterized in that the second Kurbelstelzen (96, 97) in the region between the respective push rod (37, 38) and the balancing mass (91) via a second support strut (141 , 142) are held articulated on the frame upper part (13). Pressing, stamping or forming machine according to claim 15, characterized in that the second support struts (141, 142) are articulated in the longitudinal direction of the respective second Kurbelstelze (96, 97) centrally to the second Kurbelstelze (96, 97). Pressing, stamping or forming machine according to claim 15 or 16, characterized in that the second Kurbelstelzen (96, 97) are twice as long as the second support struts (141, 142). Pressing, stamping or forming machine according to claim 15, 16 or 17, characterized in that the second support struts (141, 142) are the same length as the first support struts (45, 46). Pressing, punching or forming machine according to one of claims 15 to 18, characterized in that in each case a first and a second Support strut (45, 141, 46, 142) at a common pivot point (58, 59) are pivotally connected to the frame top (13). Pressing, stamping or forming machine according to one of the preceding claims, characterized in that the plunger (18) and / or the compensating mass (91) by means of guide columns (19; 92) and associated guide bearings (20, 21; 93, 94) displaceable are held. Pressing, punching or forming machine according to claim 20, characterized in that the guide columns (19) of the plunger (18) on the plunger (18) are fixed and the associated guide bearings (20, 21) on the frame (11) are held. Press-stamping or forming machine according to claim 20, characterized in that the guide columns (92) of the balancing mass (91) on the frame (11) and the associated guide bearings (93, 94) are held on the balancing mass (91). Pressing, stamping or forming machine according to claim 21, characterized in that on the plunger (18) fixed guide columns (19) above and below a strip running plane (23) by means of a sliding or Wälzkörperführung (20, 21) are slidably mounted. Pressing, punching or forming machine according to one of the preceding claims, characterized in that the thrust units (32, 33) have an adjusting device (55) for adjusting the position of the lower Dead center of the plunger (18) during operation of the pressing, punching or forming machines. Pressing, stamping or forming machine according to claim 24, characterized in that the thrust units (32,33) each have two mutually cooperating thrust arms (48, 49) which are mutually displaceable by means of the adjusting device (55) in the vertical direction. Pressing, stamping or forming machine according to claim 25, characterized in that the two push arms (48, 49) via a thread (50) are interconnected, wherein at least one end portion of a push arm (49) by means of the adjusting device (55) relative to another thrust arm (48) is rotatable about the thread axis.

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