EP0316475B1 - Press, in particular for making dimensionally stable pressed articles from powdery materials - Google Patents

Abstract

The press can be equipped or used, as required, for executing the so-called pull-off method and the so-called counterpressing method. It has a press body 103 in which a press frame 105 and a press table 104 as main and guiding axis are provided, which are coupled to one another with movement engagement by means of a mechanical drive, primarily a toggle lever drive 106 and form a main press ram. It furthermore has a lower ram 114 which is assigned to the press table 104 as pull-off ram and/or counterpressing ram and is actuated by means of a lever 123 which is mounted swivellably in the press body 103 and can be moved by a mechanical drive 111, in particular a cam or eccentric drive. <??>The lever used is a two-armed lever 123 whose one arm 124 acts on the lower ram 114, while its other arm 125 is connected in articulated manner with an intermediate lever 133 which in turn is seated on a rocker shaft 134a, 134b lying in the press body 103. The rocker shaft 134a, 134b can be coupled selectively or reciprocally with two different gear trains of the mechanical drive 111, the one gear train being designed for carrying out the pull-off method and the other gear train being designed for carrying out the counterpressing method. <IMAGE>

Description

The invention relates to a press which can be used, in particular, for producing dimensionally stable compacts from powdery materials, but which is also suitable for other uses, for example in the fields of plastics pressing technology, deep-drawing technology and stamping technology.

The subject of the invention is a press with a press frame, in which a press frame and a press table are provided as the main and leading axis, which are coupled to one another by a mechanical drive, primarily a toggle lever drive, and form a main press ram, and above is also provided with a lower plunger assigned to the press table as a pulling plunger and / or counter-pressing plunger, which can be actuated by a lever which is pivotally mounted in the press frame and can be moved by a mechanical drive, in particular a cam or cam drive.

Presses of this type have already been developed and are described, for example, in European patent applications EP-A-0289638 and EP-A-0305566.

The presses based on this development not only ensure that all of the cooperating press axes can always be perfectly reproduced, they can can also be operated with relatively high stroke rates. A high degree of dimensional stability of the entire press system is maintained with a permanently high level of functional reliability.

It is particularly advantageous that a press system has been created that can only be realized using an existing mechanical press, in particular a toggle press, by integrating an additional hydraulic press part. At the same time, flexible movement and drive options for the individual presses are achieved and, in addition, pressure-independent path control of the same is made possible.

The mechanical press part of the press according to European patent application EP-A-0289638, and preferably the press table, is also assigned an additional lower plunger which can be actuated by a mechanical drive, namely preferably a cam or cam drive. This lower plunger forms the so-called G-press axis, which makes it possible to work with the press either according to the so-called counter-pressing process or also according to the so-called pull-off process, in which case the lower plunger either forms the press counter-plunger or the press pulling plunger.

The invention aims at a press of the initially specified type to optimize the mechanical press part which actuates the ram and functionally in a structurally simple configuration. The object of the invention is therefore to design the functional parts of the mechanical press part which actuates the lower plunger in such a way that it can be easily adapted to the respective needs and, if necessary, can also be retrofitted at any time for changing needs. So it depends on an assembly system for generic presses Specify which equipment and / or retrofit options ensure that the operation of the lower ram either only in the pull-off process or only in the counter-press process, but which also allow the alternate or alternative operation for the pull-off and the counter-press process.

Essential to the invention to achieve this object is that - according to the characterizing part of claim 1 - the lever is a two-armed lever, one arm of which engages the lower plunger, while its other arm is articulated to an intermediate lever, which in turn is supported on a press frame Vibrating shaft sits, and that the vibrating shaft can be coupled via one or the other of two different gear trains with one and the same mechanical drive.

The advantage of this design according to the invention is that, in the simplest case, only the gear train required in each case is installed in the press between the mechanical drive and the lower plunger, in such a way that it either only the gear train for operating the lower plunger during the triggering process or only the gear train contains for the operation of the lower ram in the counter-pressing process. It is also possible to alternately install the two different gear trains in the press or to equip the press with both gear trains at the same time at any time, so that it can be used as desired for the triggering process or the counterpressing process. In the latter case, the oscillating shaft can then optionally and alternately be coupled with two different gear trains of the mechanical drive.

According to a further feature of the invention, the two gear trains each consist of at least one that can be selectively coupled and uncoupled to the oscillating shaft Lever as well as at least from a rotating, driven cam or cam disc engaging there, all cam or cam discs sitting on a common drive shaft, which preferably also carries a drive crank for a toggle lever drive, which forms the actual drive for the main press ram.

Another important design measure according to the invention - according to claim 3 - is also that the effective length of the intermediate lever and / or the articulated arm of the two-armed lever is infinitely adjustable so that the stroke of the lower plunger can vary in a simple manner at any time leaves. It has proven useful if - according to claim 4 - the transmission ratio of the intermediate lever to the two-armed lever can be varied continuously over a range from 0 to 1: 2.5.

To vary the gear ratios, the invention proposes - according to claim 5 - that the connecting joint of the intermediate lever to the two-armed lever is seated in sliding blocks and is displaceable therein via a spindle actuator which is located on or in the second arm of the two-armed lever. These measures create the possibility of a remotely controllable change in the gear ratio.

It is - according to claim 6 - proposed as a further inventive measure to design the lever of one gear train as an angle lever, one arm of which is assigned a drive cam on the drive shaft, while its other arm is in the effective range of a locking shaft also seated on the drive shaft. Cam protrudes. In this way, a positive positive control of this gear train is guaranteed, namely for the angular range of a curve that corresponds to the pressing position of the upper punch in the bottom dead center position of the X axis. The press die, which is moved downward during the press travel depending on the X-axis, for example hydraulically, is thus provided with a stop fixation via the two-armed lever.

It is particularly advantageous according to the invention - according to claim 7 - if the angle lever of one gear train is kept in constant contact with the locking cam disc by a pressure medium cylinder, for example a hydraulic cylinder. In contrast, the lever of the second gear train is - according to claim 8 - a one-armed lever which protrudes into the effective area of a second drive cam disc and with this by a pressure medium cylinder, e.g. a hydraulic cylinder, is kept in constant contact.

Another important embodiment of the invention is - according to claim 9 - that the two-armed lever and the intermediate lever in the direction of a predetermined basic position by a pressure medium cylinder, e.g. a hydraulic cylinder, can be acted upon, and that in this basic position the coupling device between the oscillating shaft and the levers of the two gear trains sitting thereon can be engaged and disengaged.

It has proven itself according to the invention if, according to claim 10, the coupling devices each consist of coupling drivers, which are non-rotatably wedged onto the oscillating shaft, and of coupling slides, which are guided on the levers in an adjustable manner transversely to their plane of movement and which are inserted by pressure medium cylinders, for example hydraulic cylinders. and can be disengaged. It is expedient if, according to claim 11, the coupling driver has engagement holes, for example bushings, provided arms, while the clutch slider are formed by cross-section push pins. According to the invention, these coupling slides or push pins of the coupling devices can be designed as overload protection devices, for example provided with predetermined breaking points.

Within the scope of the invention it is further proposed, according to claim 13, that the short arm of the two-armed lever articulates via a limitedly displaceable intermediate piece on a pressure piece, which in turn is guided in the lower tappet parallel to its direction of movement to a limited extent, with adjustment stops between the pressure piece and the lower plunger, via which the extent of the relative displacement can be changed.

According to the invention - according to the proposal of claim 14 - an adjustment stop can be assigned to each end of the pressure piece, both adjustment stops being selectively activated by their own drive, e.g. an electromechanical drive.

It has also proven to be advantageous if, according to the invention - according to claim 15 - the intermediate piece forms a carriage which can be shifted in height in the table console and which is provided with coupling elements for the lower tappet which can be engaged and disengaged in the transverse direction.

Finally, it has also proven to be important according to the invention that - according to claim 16 - the lower plunger drive is associated with a hydraulic press part installed between the press frame and press table with at least one additional press axis, but preferably several additional press axes, in which the working movement is assigned to everyone Press axis of the hydraulic press part away and time-dependent on the working movement of the main and leading axis of the mechanical press part consisting of press frame and press table.

The press according to the invention makes a number of different functions of the lower plunger possible.

When working according to the so-called pull-off method in connection with the hydraulic press part, the pull-off movement in the downward direction can be effected with a force of, for example, Pmax = 2000 kN. A trigger stroke can be set, which can be varied, for example, between 0 and 80 mm. Any necessary corrections to the height of the lower plunger can be made using an electromagnetic actuator on the extension piece. A mechanical fixation of the lower plunger in the pressed position can also be brought about by the locking cam. In addition, electromechanical adjustment of the lower plunger is possible on the one hand in its pressing position and on the other hand in its filling position.

For the counter-pressing method, the counter-pressing movement in the upward direction can be carried out with a force of Pmax = 2000 kN and then the ejection movement is carried out. Here too, the stroke of the lower plunger can be infinitely adjusted, for example over a range from 0 to 80 mm, and an electromechanical adjustment can be effected both for the pressing position and for the filling position.

If both gear trains are present in the press, the presses can be switched from the pull-off method to the counter-pressing method and vice versa.

Both for the pull-off method and for the counter-pressing method, the push pins of the coupling devices can be designed as overload protection devices, which prevent damage to other functional parts of the press.

For the counter-pressing process, it can also prove to be advantageous if the cam disk of the gear train in question is easily replaceable on the drive shaft, so that the lifting movement of the lower plunger can be easily adapted to different needs.

All other functions of the press during the pull-off process, such as lowering the press die, the electromechanical adjustment of the start of lowering, the upward provision of the lower plunger and the height adjustment of the upper connecting piece are preferably effected via the hydraulic press part of the press system.

All functions of the press can either be operated individually from a control panel, for example by pressing a button. However, they can also be set and operated automatically by a computer program using a tool code.

• Figur 1 von der Seite gesehen und im Vertikalschnitt entlang der Linie I-I in Fig. 3 den erfindungswesentlichen Bereich des mechanischen Prssenteils eines -bspw. für hydromechanischen Betrieb ausgelegten -Pressensystems,
• Figur 2 den erfindungswesentlichen Bereich des mechanischen Pressenteils nach Fig. 1 in Pfeilrichtung II-II der Fig. 3 gesehen,
• Figur 3 teilweise in Ansicht und teilweise im Schntit entlang der Linie III-III in Fig. 2 und
• Figur 4 eine Ansicht der Presse in Pfeilrichtung IV der Fig. 1.

In the drawing, the object of the invention is shown in one embodiment. Show it

• Figure 1 seen from the side and in vertical section along the line II in Fig. 3, the area essential to the invention of the mechanical press part of a - for example. press system designed for hydromechanical operation,
• FIG. 2 seen the area of the mechanical press part according to FIG. 1 that is essential to the invention in the direction of arrow II-II of FIG. 3,
• Figure 3 partly in view and partly in section along the line III-III in Fig. 2 and
• FIG. 4 is a view of the press in the direction of arrow IV in FIG. 1.

In the drawing, of a hydromechanical press system 101, essentially only the mechanical press part is shown, which in turn has a toggle press 102. The mechanical press part has a press frame 103 which carries a press table 104 and in which a press frame 105 is guided so that it can be raised and lowered relative to the press table 104.

The press table 105 is moved in the press frame 103 via a toggle lever system 106 which engages on the one hand via a joint 107 on the press frame 103 and on the other hand via a joint 108 on the press frame 105. A push rod 110 is in drive connection with the knee joint 109 of the toggle lever system 106, which can be formed, for example, by the crank pin of a crank mechanism 111, which is accommodated in the press frame 103.

The push rod 110 is thereby moved by the drive in a fixed 360 ° travel-time curve in such a way that the toggle lever system 106 continuously carries out alternating movements between its extended position (FIG. 1) and a predetermined bent position. Thus, the press frame 105 runs through a precisely defined, relatively large stroke path relative to the press table 104.

A hydraulic press part 112 is adapted into the mechanical press part, which is designed as a toggle press 102, namely between the fixed press table 104 and the press frame 105 that can be raised and lowered, but is only partially shown in FIGS. 1 and 4. The actual pressing tool 113 is also only hinted at in FIGS. 1 and 4.

The main press ram of the hydromechanical press system 101 is formed by the cooperation of the press table 104 and the press frame 105 of the toggle press 102 and is effective as the so-called main or leading axis - the so-called X axis - for the entire hydromechanical press system 101.

Further additional press axes of the hydromechanical press system 101, namely, for example, the so-called M press axis, the so-called Z press axis and the so-called Y press axis (which are not important for the object described here) can be formed by the hydraulic press part 112.

On the other hand, it is essential for the mechanical equipment of the hydromechanical press system 101 that, in addition to the toggle lever press 102 forming the so-called main or leading axis - the so-called X-axis - there is also another mechanical press axis - the so-called G-press axis. The drive for this G-press axis is derived from the crank mechanism 111 for the toggle press 102.

The G press axis works with a lower plunger 114, which can only be seen in FIGS. 1 and 4 of the drawing. It consists of a carriage 115, which can be displaced to a limited extent in the table bracket 103 as an intermediate piece, and a carriage 115 that can be inserted and disengaged in the transverse direction Coupling elements 116 for a vertical movement related extension piece 117 which leads up through the press table 104 so that it can cooperate with the pressing tool 113 or the like.

4 of the drawing, the slide 115 of the lower plunger 114 has a frame-like shape, a pressure piece 119 engaging in its frame opening, which is penetrated in the transverse direction by a bearing pin 120. Sliders 121 sit on both ends of the pressure piece 119 on the ends of the bearing bolt 120.

In the press frame 103, a two-armed lever is pivotally supported on a vertical plane to a limited extent about a horizontal transverse axis 122, the short arm 124 of which is fork-shaped and, as can be seen from FIG. 4, with its two fork legs 124a and 124b past the pressure piece 119 into the Frame opening 118 of the slide 115 protrudes. Both fork legs 124a and 124b of the short arm 124 have a link slot 126, in which one of the two sliding pieces 121, which are seated on the bearing pin 120, is accommodated in a longitudinally displaceable manner.

The long arm 125 of the two-armed lever 123 is also equipped with a link slot 127, which extends over most of its length and serves as a guide receptacle for a slide 128. In this slider 128, a hinge pin 129 is arranged so that it protrudes on opposite sides over the slider 128. In turn, a slider 130a or 130b is articulated on each end of the hinge pin 129 and is slidably received in a link slot 131a or 131b. These link slots 131a and 131b are each located on the inside of two cheeks 132a and 132b of an intermediate lever 133. Both cheeks 132a and 132b of the intermediate lever 133 have an angled outline shape and are connected in one piece or in the same material to a bracket in the end region of their one angle leg by a cross piece 132c. The slot slots 131a and 131b extend parallel to the longitudinal direction of the other angle leg of both cheeks 132a and 132b.

On the outside, each cheek 132a and 132b of the intermediate lever 133, 134a and 134b connects in one piece and in a manner fixed against relative rotation, in such a way that the longitudinal central axes thereof not only align with one another, but also pass through the intersection of the two longitudinal central planes of the angle legs of both cheeks 132a and 132b. But also the longitudinal center plane of the slot slots 131a and 131b intersect the longitudinal axes of the two oscillating shafts 134a and 134b.

Via the slider 128, the hinge pin 129 and the sliders 130a and 130b, the intermediate lever 133 is connected via its link slots 131a and 131b and the two-armed lever 123 via the link slot 127 in its long arm 125 in an articulated drive connection, in such a way that any swinging movement of the intermediate lever 133 is inevitably transferred to the two-armed lever 123.

The transmission ratio of the transmission of movement from the intermediate lever 133 to the two-armed lever 123 can be varied, preferably over a range that includes the value 0 and up to a transmission ratio of 1: 2.5. A spindle actuator 135, which is installed in the long arm 125 of the two-armed lever 123, and whose spindle acts on the slider 128 serves for the stepless adjustment or change of this transmission ratio. By actuating the spindle actuator 135, the sliding pieces 128 and 130a, 130b are moved together in the slot slots 127 and 131a, 131b, so that the transmission ratio changes in accordance with the respective sliding position. If the setting is made so that the longitudinal axis of the hinge pin 129 is in alignment with the longitudinal axis of the oscillating shafts 134a and 134b, then the intermediate lever 133 can execute oscillating movements with its oscillating shafts 134a and 134b without any movement being transmitted to the two-armed lever 123. In this case the gear ratio is 0.

From Fig. 3 of the drawing it can be seen that the intermediate lever 133 is held by its two oscillating shafts 134a and 134b in fixed bearings 137a and 137b of the press frame 103. The oscillating shafts 134a and 134b protrude from both bearings 137a and 137b by a considerable amount. In the direct connection to the bearings 137a and 137b arms 138a and 138b are non-rotatably wedged onto the oscillating shafts 134a and 134b, which can be used as a coupling driver in a manner to be described.

The intermediate lever 133 can be driven by the oscillating shafts 134a and 134b by means of two different gear trains 139a and 139b, which have their main drive in common with the crank mechanism 111 for the toggle lever mechanism 106.

The gear train 139a shown on the left in FIG. 3 can also be seen in FIG. 1 of the drawing, while the gear train 139b shown on the right in FIG. 3 is further shown in FIG. 2.

The gear train 139a comprises a drive cam 140, which is non-rotatably wedged on the drive shaft of the crank drive, and a locking cam 141, which is also non-rotatably seated on this shaft, and an angle lever 142 which is on the left end portion of the left swing shaft 134a of the intermediate lever 133 is held, as can be seen in FIG. 3. The angle lever carries a roller 144 at the free end of its arm 143a and a roller 145 at the free end of its arm 143b. While the roller 144 interacts with the cam contour of the drive cam 140, the roller 145 is the circumferential contour of the locking cam 141 assigned.

From Fig. 1 it can be seen that over a certain angle of rotation of the drive shaft on the one hand, the roller 144 of the arm 143a and on the other hand the roller 145 of the arm 143b at the same time rest on the circumferential contour of the drive cam 140 and locking cam 141, so that the angle lever 142 is locked against movement. As soon as and as long as the roller 145 of the arm 143b comes out of contact with the locking cam 141, however, the drive cam 140 causes the pivoting of the angle lever 142 about the longitudinal axis of the oscillating shaft 134a via the roller 144 and the arm 143a. However, as long as the angle lever 142 has no coupling connection with the oscillating shaft 134a, it cannot transmit its movement to the intermediate lever 133. Rather, for this purpose it must be brought into engagement with the arm 138a serving as a clutch driver on the oscillating shaft 134a. For this purpose, a push pin 146 serving as a clutch slide is used, which is seated in a guide housing 147 on the angle lever 142 and can be displaced with the aid of a pressure medium drive, namely in particular a hydraulic cylinder 148. In the retracted position of the thrust pin 146, the latter is disengaged from the coupling sleeve of the arm 138a so that the angle lever 142 can be moved freely about the oscillation axis 134a, whereby it can optionally be held in contact with the drive cam plate 140 by a pressure medium cylinder . However, if the push pin 146 is engaged, then the pivoting movement is transmitted to the oscillating shaft 134a via the arm 138a. The movement transmitted from the angle lever 142 to the oscillating shaft 134a then also occurs with the intermediate lever 133 and thereby also forcibly moves the two-armed lever 123.

The gear train 139b shown on the right-hand side of FIG. 3 has a drive cam plate 150 which is connected to the drive shaft for the crank mechanism 111 and which interacts with a lever 151 via a roller 152, as can be clearly seen in FIG. 2. The lever 151 is suspended on the right end of the right oscillating shaft 134b, as can be seen easily from FIG. 3. Here, too, the suspension is normally provided to be relatively movable, i.e. the lever 151 can easily be angularly displaced relative to the oscillating shaft 134b as long as the push pin 154, which is guided in a guide housing 153 of the lever 151 as a coupling slide, is in its disengaged position shown in FIG. 3. If, on the other hand, this push pin 154 is inserted axially into the coupling sleeve 156 of the arm 138b, which is non-rotatably wedged onto the oscillating shaft 134b by an actuator designed as a hydraulic cylinder 155, as is indicated by dash-dotted lines, then the movement of the lever 151 of the oscillating shaft 134b and over can these are transmitted to the intermediate lever 133.

Of course, precautions are taken to prevent both push pins 146 and 154 from being simultaneously brought into their engagement position by their hydraulic cylinders 148 and 155. These precautions can consist in that each of the two hydraulic cylinders 148 and 155 can only be acted upon in the direction of engagement if both push pins 146 and 154 are in their actuation time Disengagement. If, on the other hand, one of the two push pins 146 and 155 is engaged, then the other must not be able to be acted upon in the sense of engagement.

In order to ensure that when the press is at a standstill, the push pins 146 and 155 can be properly engaged and disengaged, a hydraulic cylinder 157 engages on the two-armed lever 123, which is supported on the press frame 103. He acts on the two-armed lever 123 in such a way that this and thus also the intermediate lever 133, on the one hand, is brought into a predetermined basic position with respect to the angle lever 142 and, on the other hand, with respect to the lever 151, in which at least the pushing-in bolts 146 and 155 can properly engage .

So that the one-armed lever 151 is constantly held in contact with the circumferential contour of the associated drive cam 150 via its roller 152, a hydraulic cylinder 158 is also supported on the press frame 103, the piston rod of which engages the lever 151 and pushes it in the direction toward the drive cam 150 keeps under tension.

It should be mentioned here that the drive device for the lower plunger 114 of the mechanical press part does not in principle have to be equipped with the two drive trains 139a and 139b for the intermediate lever 133. Rather, it is also easily possible to provide either only the gear train 139a or only the gear train 139b. However, the gear train that is not available can be retrofitted into the press at any time, should this be necessary. It is also easily conceivable to remove the gear train contained in the press and instead to install the gear train that was not previously available.

A hydromechanical press system 101, which is to be operated both by the so-called pull-off method and by the so-called counter-press method, is expediently equipped with two gear trains 139a and 139b for the intermediate lever 133 from the outset.

In any case, the gear train 139a is intended for the operation of the hydromechanical press system 101 according to the so-called pull-off method, while the gear train 139b enables the operation of this hydromechanical press system 101 according to the counter-pressing method.

Since both the pressing force and the ejection force of the lower plunger 114 act against the drive cam 150 via the intermediate lever system and the roller 152 in this counterpressing method, an additional locking cam is not necessary here.

An upper adjustment stop 159 and a lower adjustment stop 160 are assigned to the pressure piece 119 in the frame opening 118 of the slide 115. The upper adjustment stop 159 is actuated by an electromechanical drive 161, while the lower adjustment stop 160 can be actuated by a corresponding electromechanical adjustment drive 162.

While with the help of the upper adjustment stop 159 an exact adjustment of the pressing path is ensured in the pull-off method, the exact adjustment of the fill level in the pressing tool 113 can be effected with the help of the lower adjustment stop 160 both for the pull-off and for the counter-pressing method.

Claims (17)

1. A press, in particular for manufacturing true-to-size blanks from powdery materials, having a press frame (103), in which a press housing (105) and a press plate (104) are provided as the main and steering axle, which are movably connected to one another by a mechanical drive, preferably a toggle lever drive (106), and form a main press ram, and having a lower ram (114) associated to the press plate (104) as the stripping ram and/or counter-press ram, which can be actuated by a lever (123) pivoted in the press frame (103), which can be moved by a mechanical drive (111), in particular a cam drive, characterised in that the lever is a two-armed lever (123), one arm (124) of which acts on lower ram (114), whereas its other arm (125) is swivel-connected (129) with an intermediate lever (133), which in turn is supported on a swivel shaft (134a, 134b) supported in press frame (103), and in that at the same time the swivel shaft (134a, 134b) can be connected via one (139a) or the other (139b) of two different drive units (139a and 139b) to one and the same mechanical drive (111).
2. A press according to claim 1, characterised in that both drive units (139a and 139b) are simultaneously provided and in this case can be selectively and reciprocally connected to the swivel shaft (134a, 134b), in that both drive units consist of a lever (142 or 151) which can he selectively coupled or uncoupled to the swivel shaft (134a or 134b) and of at least one cam disk (140 or 150) which is driven in rotation and acts hereon, with all cam disks (140 and 150) being supported on a mutual drive shaft (111), which preferably also simultaneously supports an operating crank for a toggle lever drive (106), which forms the actual drive for the main press ram.
3. A press according to one of Claims 1 to 2, characterised in that the effective length of the intermediate lever (133) and/or of the arm (125) of the two-armed lever (123) which is swivel-connected thereto can be continuously varied.
4. A press according to one of Claims 1 to 3, characterised in that the transmission ratio of the intermediate lever (133) to the two-armed lever (123) can be continuously varied over a range of 0 to 1:2.5.
5. A press according to one of Claims 1 to 4, characterised in that the connecting joint (129) of the intermediate lever (133) to the two-armed lever (123) is supported in sliding blocks (127; 131a, 131b) of said press and can be displaced therein via a variable spindle drive (135), which is located on or in the second arm (125) of the two-armed lever (123).
6. A press according to one of Claims 1 to 5, characterised in that the lever of one drive unit (139a) is an angle lever (142), to one arm (143a) of which on drive shaft (111) a drive cam disk (140) is assigned, whereas its other arm (143b) protrudes into the effective region of a locking cam disk (141) also supported on drive shaft (111).
7. A press according to one of Claims 1 to 6, characterised in that the arm (143a) of angle lever (142) is kept in permanent contact with the drive cam disk (140) by a pressure medium cylinder, e.g. a hydraulic cylinder.
8. A press according to one of Claims 1 to 7, characterized in that the lever (151) of the second drive unit (139b) is a one-armed lever, which protrudes into the effective region of a second drive cam disk (150) and is kept in permanent contact therewith by a pressure medium cylinder (158), e.g. a hydraulic cylinder.
9. A press according to one of Claims 1 to 8, characterised in that the two-armed lever (123) and the intermediate lever (133) can be loaded in the direction of a prescribed basic position by a pressure medium cylinder (157), e.g. a hydraulic cylinder, and in that in this basic position the coupling devices (146 to 149 and 153 to 156) can be engaged and disengaged between the swivel shaft (134a, 134b) and the levers (142 and 151) of the two drive units (139a and 139b) supported thereon.
10. A press according to one of Claims 1 to 9, characterised in that the coupling devices (146 to 149 and 153 to 156) respectively consist of coupling carriers (138a, 138b) wedged onto swivel shaft (134a, 134b) so that they can not rotate and also of coupling slides (146, 154) adjustably guided on the levers (142 and 152) at right angles to their plane of movement, with it being possible to engage and disengage said slides by pressure medium cylinders (148, 155), e.g. hydraulic cylinders.
11. A press according to one of Claims 1 to 10, characterised in that the coupling carriers (138a and 138b) consist of arms provided with coupling sleeves (149, 156), whereas the coupling slides are formed by thrust bolts (146, 154) having identical cross sections.
12. A press according to one of Claims 1 to 11, characterised in that the coupling slides or thrust bolts (146, 154) of the coupling devices form overload safety devices, e.g. are provided with safety points.
13. A press according to one of Claims 1 to 12, characterised in that the short arm (124) of the two-armed lever (123) acts on a thrust piece (119) via a sliding contact (121) with limited displacement, and said thrust piece is in turn guided parallel to its direction of adjustment with limited displacement, with adjustable stops (159, 160) being supported between the thrust piece (119) and the lower ram (114), via which the extent of the relative displacement can be altered.
14. A press according to one of Claims 1 to 13, characterised in that an adjustable stop (159, 160) is assigned to each end of the thrust piece (119), and in that both adjustable stops (159, 160) can be selectively actuated by an intrinsic drive, e.g. an electromechanical drive (161, 162).
15. A press according to one of Claims 1 to 14, characterised in that the intermediate piece forms a carriage (115), which is vertically displaceable in the console (103) and which is provided with coupling components (116) for the lower ram (117), which can be engaged and disengaged in the transverse direction.
16. A press according to one of Claims 1 to 15, characterised in that the lower ram is assigned to a hydraulic press part (112) installed between press housing (105) and press plate (104) and having at least one additional press axle, but preferably several additional press axles (M press axle, Z press axle and Y press axle), in which the operating movement of each press axle of the hydraulic press part (112) can be controlled and regulated as a function of the path and time of the operating movement of the main and steering axle (X axle) of the mechanical press part (102) consisting of press housing (105) and press plate (104).
17. A press according to one of Claims 1 to 16, characterised by forced control for one drive unit (139a) over one angular region of a cam rotation, which corresponds to the press position of the upper die in the lower dead-centre position of the X axle.

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