EP3115190A1 - Device and method for controlling the principal drive of a precision cutting press - Google Patents

Abstract

The invention relates to an apparatus and a method for controlling the main drive of a hydraulically driven fineblanking press. The object of the invention is to provide an apparatus and a method for controlling the main drive of a hydraulically driven fineblanking press whose hydraulic circuit simplified by eliminating hydraulic lines, the amount of hydraulic fluid can be reduced while increasing the number of strokes with simple construction of the press. This object is achieved in that the main piston (20) discus-like projecting work surfaces (22a, 22b) which in the master cylinder space (19) superimposed on the first (upper) and second (lower) pressure chamber (23a, 23b) with a small stroke, associated with the hydraulic system (18) in communication first (upper) fluid channels (24a, 24b, 24c, 24d) and second (lower) fluid channels (24e, 24f, 24g, 24h) in the foot piece (5), wherein the fluid channels (24a to 24d) with the fluid channels (24e to 24f) by a respective foot piece (5) arranged bypass channel (26) are connected to these channels (24a to 24h) and the pressure chambers (23a, 23b) an internal hydraulic system forms, in rapid traverse by pressure-controlled proportional valves (25a, 25b, 25c, 25d) when displacing the hydraulic fluid from the first to the second pressure chamber (23a, 23b) is opened and closed in the power stroke, and that during the power stroke at least a second Fluidka Nal is a Kraftstubkanal and the first pressure chamber (23a) with a discharge channel (29) is connected, said fluid channel for supplying hydraulic fluid predetermined pressure in the second pressure chamber (23b) with a supply channel (32) and branch channel (33) and the discharge channel (29) for discharging the displaced from the first pressure chamber (23 a) hydraulic fluid via a tank valve (30) with a collecting tank (44) are in communication.

Description

The invention relates to a device for controlling the main drive of a hydraulically driven fineblanking press, with a arranged in the foot master cylinder, in which the pressure chambers with hydraulic fluid acted upon, a lifting movement between UT and OT in the direction Hubachse exporting and a table top carrying main piston / plunger is performed, with guided in Schnellhubzylinders, pressurized with hydraulic fluid pressure chambers double-acting Schnellhubkolben with piston rods for rapid traverse / Tasthub of the main piston and table top and with at least one hydraulic pump unit comprehensive hydraulic system for supplying the pressure chambers with the set to a predetermined working pressure by a central control hydraulic fluid.

The invention further relates to a method for controlling the main drive of a hydraulically driven fineblanking press guided in a master cylinder of the foot, carrying a table top main piston, which performs a lifting movement between UT and OT, in which the main piston arranged with table top by pressurizing the pressure chambers of a Schnellhubzylinder Schnellhubkolbens in rapid traverse / Tasthub between UT and OT or OT and UT is moved, then the rapid traverse / Tasthub terminated and then the main piston in the power stroke performs the cutting or forming operation, the pressure chambers of the main piston with a predetermined by a central control and by a Hydraulic pump unit generated working pressure of a hydraulic fluid from a hydraulic system can be acted upon.

State of the art

The fineblanking process requires special triple-action presses that basically operate from the bottom up, allowing controlled control of the cutting process with the auxiliary functions for the ring point, anvil and ejector. The ring-tooth force and counter-holding force are generated hydraulically and the cutting force is generated mechanically or hydraulically.

There are a variety of piston assemblies that are used in presses for driving or pressurizing.
According to the state of the art DE 2 218 476 A1 and DE 2 264 429 A1 it is a fine stamping press with two rigidly interconnected frame bodies, to which two to Clamping two tool parts serving, hydraulically axially towards each other and away from each other displaceable table body are mounted. In the first frame body, a cylinder space is provided, in which two coaxial, with respect to each other movable piston are arranged, of which the first is connected to a piston rod and the second surrounds this piston rod and forms a part of the first frame body displaceably removed, first table body. The second piston has an internal thread and is screwed onto an externally threaded bush, so that the axial position of the second piston is adjustable.

From the DE 195 24 042 is a method for controlling the drive, in particular a hydraulic press for forming and / or cutting of sheets with at least one double-acting piston-cylinder unit for driving a press ram known. This press works in the direction of gravity, ie from top to bottom. In a first working phase of the press during the downward movement of the unloaded press ram, the upper and lower cylinder space of the piston-cylinder unit is connected via a valve device. For the subsequent forming phase of the press, a motor / pump device with a volume-controllable hydraulic motor / pump device is provided, which is driven at least via a rechargeable storage system and whose controllable torque can be fed to a controllable pump device. In the DE 198 22 436 A1 A method of operating a hydraulic press is described in which the force required for the deformation of a workpiece is applied by the piston of a double-acting cylinder and this force is applied via mechanical intermediate links of the piston transferred to a press tool, wherein the pressing tool impinges only after passing through a first path on the workpiece and is then formed during the passage of a second distance. The press works from top to bottom and the rapid traverse is essentially brought about by the dead weight of the press beam when pressure is relieved.

The DE 10 2012 006 981 A1 discloses a hydraulic press with a plunger, which is adjustable by means of a hydraulic drive device, wherein the hydraulic drive device comprises a working cylinder in which a drive piston is slidably received, which divides the interior of the drive cylinder into a first working chamber and a second working chamber, which with a Hydraulic fluid can be acted upon. At least one hydraulic return device is provided to bring the plunger after the forming operation in its initial position.
The basic idea of this known prior art is to derive the hydraulic fluid during the forming process from the second working chamber via a pump in the storage tank.

To provide rapid traverse cylinder during the delivery stroke of the press ram, are known from a variety of solutions ( DE 196 43 635 A1 . DE 197 41 879 A1 . DE 198 22 436 A1 . DE 102 15 003 A1 . DE 10 2004 006 126 B4 . DE 10 2009 058 407 A1 . EP 0 311 779 B1 . EP 0 615 837 B1 . EP 891 235 B1 .)
In all of these known solutions, the main piston and the rapid-action piston belong to separate hydraulic circuits, in which the displaced from the work spaces Hydraulic fluid as the pistons move down either into a tank ( DE 10 2009 058 407A1 ) or from the upper working space to the lower working space ( DE 10 2004 006 126 B4 . DE 196 42 635 A1 . DE 102 15 003 A1 . EP 0 891 235 B1 ) are rearranged.
This shift takes place in separately installed hydraulic lines and independent of the position of the quick-lift pistons in the quick-lift cylinder. The Schnellhubzylinder are basically arranged on the head of the press and therefore must be able to carry the entire upper structure of the press including Traverse and to lift the Zustellhub. The main drive / plunger of these known presses is equipped with no rapid traverse or Schnellhubzylinder, so that the cycle time or the achievable number of strokes is correspondingly low.

task

In this prior art, the present invention seeks to provide an apparatus and a method for controlling the main drive of a hydraulically driven fineblanking press, simplifies the hydraulic circuit by eliminating hydraulic lines and reduces the hydraulic fluid amount while increasing the number of strokes with simple construction of the press can be.

This object is achieved by a device of the type mentioned above with the features of claim 1 and by a method having the features of claim 10.

Advantageous embodiments of the invention Apparatus and method are the dependent claims.

The solution according to the invention is based on the knowledge of displacing the hydraulic fluid in the pressure chambers of the main piston during the rapid traverse / key stroke during delivery in the stroke direction of the quick-lift pistons from one pressure chamber into the other pressure chamber of the main piston.
This is achieved in that the main piston discusscheibenartig projecting work surfaces, the superimposed in the master cylinder space the first (upper) and second (lower) pressure chamber with low lift, which communicating with the hydraulic system in connection first (upper) fluid channels and second (lower) Fluid channels are assigned in the foot piece, wherein the first fluid channels are connected to the second fluid channels by a respective arranged in the foot bypass channel, which forms an internal hydraulic system with these channels and the pressure chambers, in rapid traverse by pressure-controlled proportional valves when displacing the hydraulic fluid from the first is opened in the second pressure chamber and closed in the power stroke, and that during the power stroke, at least one second fluid channel is a Krafthubkanal and the first pressure chamber is connected to a discharge channel, said fluid channel for supplying hydraulic fluid predetermined Dru cks in the second pressure chamber with a supply channel and branch channel and the discharge channel for discharging the displaced from the first pressure chamber hydraulic fluid via a tank valve with a collecting tank in connection.

According to another preferred embodiment of Device according to the invention is provided that the second pressure chamber of the main piston is connected to the hydraulic pump unit during power stroke via a safety valve, at least one pressure sensor for pressure detection, at least one pressure relief valve to limit the pressure of the flow and a proportional valve for adjusting the flow rate.

In a further preferred embodiment of the device according to the invention, the main piston may have the same or different sized work surfaces, whereby both constant velocity piston and other pistons can be used depending on the application.

It is also advantageous if the proportional valves and the tank valve are pressure-controlled cartridge valves.

A further preferred embodiment of the device according to the invention provides that the quick-lift piston divides pressure chambers with different sized effective surfaces in the quick-lift cylinder, which are connected via channels arranged in the footpiece to the hydraulic system, wherein the pressure chamber with the larger effective area in a hydraulic train of non-returnable check valve, 3-way proportional valve, controllable proportional valve and high-pressure accumulator integrated and the pressure chamber with the smaller effective area via the 4/3-way proportional valve is connected to the collecting tank.
The different large effective surfaces on the quick-lift piston make it possible to execute the rapid traverse in the upward and downward direction at different speeds. Conveniently, the larger effective surface of the quick-lift piston is associated with the upward movement.

It has proved to be advantageous that two opposite, aligned parallel to the stroke axis Schnellhubzylinder are accommodated in the foot, the piston rods are each connected to a carrier, which are each attached to one side of the table top.
The Schnellhubzylinder are pressure-sealed at the top of the foot piece, each with a lid, so that easy installation and accessibility is guaranteed.

It is also advantageous that the main piston is associated with a path-measuring unit for detecting the TDC position of the main piston and the first pressure chamber of the main piston, the tank valve to build up a counterforce to reduce the cutting stroke.

According to a preferred embodiment of the invention, the hydraulic pump unit comprises at least one proportional valve for adjusting the delivery rate, at least one pressure sensor for the control of the proportional valve and at least one pressure relief valve for limiting the pressure and attitude of the flow.

The object of the invention is further achieved by a method in that the pressure chambers of Schnellhubkolbens are fed at rapid traverse / Tasthub of a permanently pressurized high pressure accumulator and at the same time the pressure chambers of the main piston separated from the hydraulic system and connected via fluid channels and bypass channels, so that hydraulic fluid is displaced from the first pressure chamber in the second pressure chamber in the stroke direction of the quick-lift piston during the rapid traverse almost without pressure.

Of essential importance for the control of the pressure chambers of the quick-lift piston is that the working pressure in the pressure chamber of the quick-release piston with the larger effective area of the central control via a pilot operated check valve, 4/3-way proportional valve, controllable proportional valve and high-pressure accumulator and the working pressure in the pressure chamber of the quick-lift piston with the smaller effective area is set via the 4/3-way proportional valve.

In a further embodiment of the method according to the invention, the working pressure in the lower pressure chamber of the main piston at the power stroke with the central control via a controllable proportional valve, at least one pressure sensor for pressure detection, at least one pressure relief valve to limit the pressure of the flow and a proportional valve for the delivery volume and the hydraulic pump unit and the Working pressure in the first pressure chamber adjusted via the proportional valve.

It is particularly advantageous that the TDC position of the main piston is adjusted via a distance measuring system with the central control, wherein the delivery volume of the hydraulic pump unit is regulated back before reaching TDC or with the tank valve in the first pressure chamber, a back pressure is generated.

Further advantages and details arise from the description below with reference to the accompanying drawings.

embodiment

The invention will be explained in more detail below using an exemplary embodiment.

• Fig. 1 eine perspektivische Ansicht einer Feinschneidpresse mit Anschluss an das Hydrauliksystem,
• Fig. 2 eine perspektivische Ansicht des Fußstückes mit Tischplatte,
• Fig. 3 einen Schnitt des Fußstückes mit Tischplatte gemäß Linie A-A der Fig. 2,
• Fig. 4a und 4b eine perspektivische Ansicht des Fußstückes mit Darstellung der Lage der Fluidkanäle und des Entlastungskanals,
• Fig. 5 einen Schnitt des Fußstücks mit Tischplatte gemäß Linie B-B der Fig. 2,
• Fig. 6 einen Schnitt des Fußstücks mit Tischplatte gemäß'Linie C-C der Fig. 2,
• Fig. 7a und 7b schematische Darstellungen der Verdrängung des Hydraulikfluids von einem Druckraum in den anderen Druckraum des Hauptkolbens in Abhängigkeit der Hublage der Schnellhubkolben und
• Fig. 8 eine schematische Darstellung des Ablaufs des erfindungsgemäßen Verfahrens.

Show it

• Fig. 1 a perspective view of a fine blanking press with connection to the hydraulic system,
• Fig. 2 a perspective view of the foot piece with table top,
• Fig. 3 a section of the foot piece with table top according to line AA Fig. 2 .
• Fig. 4a and 4b a perspective view of the foot piece showing the position of the fluid channels and the discharge channel,
• Fig. 5 a section of the foot piece with table top according to line BB Fig. 2 .
• Fig. 6 a section of the foot piece with table top according to'Line CC the Fig. 2 .
• Fig. 7a and 7b schematic representations of the displacement of the hydraulic fluid from a pressure chamber in the other pressure chamber of the main piston in dependence of Hublage of the quick-lift piston and
• Fig. 8 a schematic representation of the sequence of the method according to the invention.

The Fig. 1 shows a perspective view of a hydraulically driven fineblanking press 1, the main piston 2 basically performs a lifting movement between a bottom dead center UT and a top dead center OT in the direction of lifting axis HU from bottom to top. The press frame 3 of the press 1 comprises a head piece 4, a foot piece 5, box-shaped hollow columns 6 and tie rods 7.

As the Fig. 2 and 3 clarify, a table top 8 is arranged on the upper side OS of the foot piece 5, which carries the tool lower part, not further shown. Approximately in the middle of the foot piece 5, two opposing parallel to the stroke axis HU aligned Schnellhubzylinder 9 are introduced, each receive a double-acting Schnellhubkolben 10 and are closed with a lid 11. The quick-lift piston 10 has a guided through the lid 11 piston rod 12 which is connected to a carrier 13 which is fixed to a side wall 14 of the table top 8. The fast-stroke piston 10 divides in the quick-lift cylinder 9 a first and second pressure chamber 15a and 15b (see also Fig. 3 ). The pressure chamber 15a and the pressure chamber 15b is connected via a respective channel 16a or 16b introduced in the foot piece 5 with the hydraulic line 17 of the hydraulic system 18 for application of hydraulic fluid, so that it is possible to move the table top 8 in rapid traverse in the direction of the head piece 4 to move vertically.

The Fig. 4a . 4b and 5 show the spatial position of the fluid channels 24a to 24h and the discharge channel 29 in the foot 5 in a transparent representation and in section along the line BB of Fig. 2 ,
In the foot piece 5, a master cylinder space 19 is formed, whose axis HA lies on the lifting axis HU of the fineblanking press and accommodates the double-acting main piston 20. The main piston 20 has a cylindrical shaft 21, which discus-like perpendicular to the axis HA projecting work surfaces 22a and 22b, which divides the master cylinder chamber 19 into a first (upper) pressure chamber 23a and a second (lower) pressure chamber 23b with low lift height, so that the Foot piece 5 is compact and has a low height.
The master cylinder chamber 19 and thus the pressure chamber 23 a is pressure-tightly closed by a cover 27, which is fastened to the foot piece 5.
The first (upper) fluid channels 24a, 24b, 24c and 24d and the second (lower) fluid channels 24e, 24f are guided in the pressure chambers 23a and 23b of the main piston 20 perpendicular to the lifting axis HU according to the height position of the pressure chambers 23a and 23b , 24g and 24h. The fluid channels 24a to 24d are connected to the fluid channels 24e to 24h by a respective bypass channel 26.
Further, in each of the second (lower) fluid passages 24e to 24h, a pressure-controlled proportional valve 25a, 25b, 25c, and 25d is employed as a cartridge valve which closes the respective bypass passage 26 when the second pressure chamber 23b is pressurized with hydraulic fluid from the hydraulic system 18 is charged.
In rapid traverse, the main piston 20 performs a corresponding stroke movement between bottom dead center UT and top dead center OT and displaces the hydraulic fluid in the first (upper) pressure chamber 23a via the first (upper) fluid channels 24a to 24d, the bypass channels 26 and the second (lower) fluid channels 24e to 24h into the second (lower) when the proportional valve 25a to 25d is open. Pressure chamber 23b. The first (upper) pressure chamber 23a, the first (upper) fluid channels 24a to 24d, the bypass channels 26, the lower fluid channels 24e to 24h and the second (lower) pressure chamber 24b thus form a closed hydraulic system which, depending on the position of the proportional valves 25a can be opened or closed until 25d, so that the first (upper) pressure chamber 23a and second (lower) pressure chamber 23b are almost depressurized and the hydraulic fluid in the second (lower) pressure chamber 23b of the main piston 20 is displaced and a fluid column in the direction of BR Schnellhubkolben 10 can be constructed during rapid traverse.
If the fast-stroke piston reaches its setpoint position in rapid traverse, the proportional valves 25a to 25d switch to the closed position and the power stroke begins, which subsequently starts with the Fig. 6 is explained in more detail.

The Fig. 6 shows the foot 5 in a further section along the line CC Fig. 2 , the position of the fluid channel 24e and the discharge channel 29 (see FIG Fig. 4a ) illustrates.
In the first pressure chamber 23a of the main piston 20, the discharge channel 29 opens and in the second pressure chamber 23b of the fluid channel 24e, which are arranged perpendicular to the lifting axis HU according to the altitude of the pressure chambers 23a and 23b superimposed.
In the discharge channel 29 is a tank valve 30 for opening and closing the discharge channel 29 as a cartridge valve used, which is in the open position, when in the power stroke, the hydraulic fluid in the pressure chamber 23a is displaced to the collecting tank 44.
The fluid channel 24e is connected to a feed channel 32 lying parallel to the stroke axis HU in the foot piece 5 and to a branch channel 33 leaving the latter, via which the hydraulic system 18, which is not shown further, is connected.

In the Fig. 7a and Fig. 7b is the displacement of the hydraulic fluid from the first (upper) pressure chamber 23a in the second (lower) pressure chamber 23b during lifting movement of the main piston 20 in the direction OT during rapid traverse shown schematically using the example of the fluid channels 24a and 24b.
The main piston 20 with table top 8 performs by the Schnellhubkolben 10 a stroke in the direction of TDC. The hydraulic fluid contained in the first (upper) pressure chamber 23a is displaced from the first (upper) pressure chamber 23a by the upward movement of the working surface 22a of the main piston 20 with the tank valve 30 closed and passes through the first fluid channel 24a, the bypass channel 26, with the proportional valve 25a open second fluid channel 24e in the lower pressure chamber 23b. The displacement is indicated by an arrow in the Fig. 7b characterized. In Fig. 7b has the Schnellhubkolben 10 reaches its upper target position, the proportional valve 25a closes, the proportional valve 30 opens and the power stroke begins.

The course of the method according to the invention is based on the Fig. 8 which shows the hydraulic train 41 for the rapid traverse and the hydraulic train 42 for the power stroke of the main piston 20.

The hydraulic train 41 includes a high pressure accumulator 34 for hydraulic fluid, a controlled by the central control 35 logical proportional valve 36 which is connected to the hydraulic system 18 via the hydraulic line 17 and the pressure level in the high pressure accumulator 34 adjusts a pressure transducer 38, a safety valve 39, a 4th / 3-way proportional valve 37 which the hydraulic fluid according to the position of the Schnellhubkolbens 10 in Schnellhubzylinder 9 on the pressure chambers 15a or 15b on or off, a lower pressure chamber 15b associated pilot-operated check valve 43 and the pressure chambers 15a and 15b of the quick-lift piston 10th
The pressure chambers 15a and 15b of the quick-lift piston 10 are supplied via the common high-pressure accumulator 34 with hydraulic fluid corresponding pressure, which is set by a corresponding control of the valve 36 from the central controller 35 as a storage charge.
As soon as the fast-stroke piston reaches its upper setpoint position in rapid traverse, the proportional valve 25a installed in the fluid channel 24e closes, the tank valve 30 opens and the 4/3-way proportional valve 37 switches to a middle position. The fluid channel 24e then assumes the function of a Krafthubkanals, is supplied in the hydraulic fluid predetermined pressure in the second pressure chamber 23b.

The Hydrauklikstrang 42 for the power stroke comprises a hydraulic pump unit 40, the at least one proportional valve 45 for adjusting the flow rate, at least one pressure relief valve 46 for limiting the pressure of the flow and at least one pressure sensor 47 for pressure detection for power limitation and passing the Pressure value is assigned to the central control 35 for controlling the pressure relief valve 46, a safety valve 48, which connects the hydraulic fluid guided in the lower pressure chamber 23 b or a pressure transducer 49 for determining the pressure value for controlling the pressure relief valve 46 to the central control is passed, and the pressure chambers 23 a and 23 b of the main piston 20th
If the main piston 20 has reached its top dead center OT, the power stroke is completed. Close the safety valve 48 for the power stroke and the tank valve 30, simultaneously open the proportional valve 25a for the fluid passage 24e and the proportional valve 37 for supplying hydraulic fluid from the high-pressure accumulator 34 and the rapid traverse sets in which the upper pressure chamber 15a of the quick-lift piston 10 with hydraulic fluid predetermined pressure is applied, so that the main piston 20 is lowered together with the table top 8 and reaches its lower target position. The 4/3-way proportional valve 37 switches so that the lower pressure chamber 15 b can be acted upon with hydraulic fluid and the quick-stroke piston 10 is moved in the direction of its upper desired position.
As soon as the fast-stroke piston reaches its upper setpoint position, a renewed power stroke commences. LIST OF REFERENCE NUMBERS Precision cutting press 1 main drive 2 press frame 3 headpiece 4 footjoint 5 hollow columns 6 tie rods 7 tabletop 8th fast-stroke 9 Schnellhubkolben 10 cover 11 piston rod 12 carrier 13 Sidewall of the tabletop 14 First (lower) pressure chamber 15a Second (upper) pressure chamber 15b Channel for 15a 16a Channel for 15b 16b hydraulic line 17 hydraulic system 18 Master cylinder space 19 main piston 20 Straight shank of 20 21 Work surfaces of 20 22a, 22b First (upper) pressure chamber of 20 23a Second (lower) pressure chamber of 20 23b First (upper) fluid channels 24a, 24b, 24c, 24d Second (lower) fluid channels 24e, 24f, 25g, 24h Proportional valve for fluid channels 24e-24h 25a, 25b, 25c, 25d Bypass channel for fluid channels 26 cover 27 relief channel 29 tank valve 30 supply channel 32 connecting channel 31 branch channel 33 High-pressure accumulator 34 Central control 35 Logical valve for 34 36 4/3-way proportional valve 37 Pressure transducer 38 Safety valve for rapid traverse 39 Hydraulic pump unit 40 Hydraulic line for rapid traverse 41 Hydrauklikstrang for power stroke 42 Unlockable check valve 43 collecting tank 44 Proportional valve of 40 45 Pressure relief valve of 40 46 Pressure transducer 47 safety valve 48 Pressure transducer 49 Movement direction of 10 BR Axis main piston HA lifting axis HU Top Dead Center OT Top of 5 OS Bottom dead center UT

Claims (13)

Device for controlling the main drive of a hydraulically driven fineblanking press, with a main cylinder space (19) arranged in the foot piece (5) in which the pressure chamber (23a, 23b) can be acted upon by hydraulic fluid, executing a stroke movement between TDC and BDC in the direction of the lifting axis (HU) and a table plate (8) carrying the main piston / plunger (20) is guided with in Schnellhubzylindern (9) guided, via pressure chambers (15a, 15b) acted upon with hydraulic fluid double-acting Schnellhubkolben (10) with piston rods (12) for the rapid traverse / Tasthub of a main piston (20) and a table top (8) and a hydraulic system (18) comprising at least one hydraulic pump unit (40) for supplying the pressure chambers (15a, 15b, 23a, 23b) with a preset working pressure through a central control (35) Hydraulic fluid, characterized in that the main piston (20) discusscheibenartig projecting work surfaces (22a, 22b) which in Hauptzylin derraum (19) one above the other, the first (upper) and second (lower) pressure chamber (23a, 23b) with a small stroke divide, with the hydraulic system (18) in communication first (upper) fluid channels (24a, 24b, 24c, 24d) and second (lower) fluid channels (24e, 24f, 24g, 24h) are associated in the foot piece (5), wherein the first fluid channels (24a to 24d) are arranged with the second fluid channels (24e to 24f) through one each in the foot piece (5) By-pass channel (26) are connected, which forms an internal hydraulic system with these channels (24a to 24h) and the pressure chambers (23a, 23b), the rapid passage through pressure-controlled proportional valves (25a, 25b, 25c, 25d) Displacing the hydraulic fluid from the first to the second pressure chamber (23a, 23b) open and closed in the power stroke, and that during the power stroke at least a second fluid channel is a Krafthubkanal and the first pressure chamber (23a) is connected to a discharge channel (29), said fluid passage for supplying hydraulic fluid of predetermined pressure into the second pressure space (23b) with a supply passage (32) and branch passage (33) and the relief passage (29) for discharging the hydraulic fluid displaced from the first pressure space (23a) via a tank valve (30 ) communicate with a catch tank (44). Device according to claim 1, characterized in that the second pressure chamber (23b) of the main piston (20) during the power stroke via a safety valve (48), at least one pressure sensor (49) for pressure detection, at least one pressure relief valve (46) for limiting the pressure of the feed stream and a Proportional valve (45) for adjusting the flow rate with the hydraulic pump unit (40) is connected. Apparatus according to claim 1, characterized in that the main piston (20) has the same or different sized work surfaces (22a, 22b) Apparatus according to claim 1, characterized in that the proportional valves (25a, 25b, 25c, 25d) and the tank valve (30) are pressure-controlled cartridge valves. Apparatus according to claim 1, characterized in that the quick-lift piston (10) divides pressure chambers (15a, 15b) with differently sized effective surfaces in the quick-lift cylinder (9) which, via channels (16a, 16b) arranged in the foot piece (5), contact the hydraulic system (18 ), wherein the pressure chamber (15b) with the larger effective area in a hydraulic line (41) from a pilot operated check valve (43), 4/3-way proportional valve (37), safety valve (39) and high-pressure accumulator (34) involved and the pressure space (15a) with the smaller effective area is connected to the catch tank (44) via the 4/3-way proportional valve (37). Device according to claim 1, characterized in that two opposing, parallel to the stroke axis (HU) aligned fast-stroke (9) are provided in the bottom nozzle (5) whose piston rods (12) each comprising a support (13) are connected, each of which at one Side wall (14) of the table top (13) are attached. Apparatus according to claim 6, characterized in that the Schnellhubzylinder (9) with a lid (11) is pressure-tight manner, through which the piston rod (12) is passed. Apparatus according to claim 1, characterized in that the hydraulic pump unit (40) at least the proportional valve (45) for adjusting the flow rate, at least the pressure transducer (47) for controlling the proportional valve (45) and at least the pressure relief valve (46) for limiting the pressure of the flow includes. Apparatus according to claim 1, characterized in that the main piston (20) is assigned a path-measuring unit for detecting the TDC position of the main piston (20) and the first pressure chamber (23a) of the main piston (20) the tank valve (30) , Method for controlling the main drive of a hydraulically driven fineblanking press with a main piston (20) guided in a master cylinder of the foot piece (5) and carrying a table top (8), which performs a lifting movement between UT and TDC, according to claim 1, wherein the main piston (20 ) with table top (8) by pressurizing the pressure chambers (15a, 15b) of a Schnellhubzylinder arranged Schnellhubkolbens (10) is moved in rapid / Tasthub between UT and OT or OT and UT, then the rapid traverse / Tasthub ended and then the main piston (20 ) performs the cutting or forming operation in the power stroke, wherein the pressure chambers (23a, 23b) of the main piston (20) with a predetermined by a central controller (35) and by a hydraulic pump unit (40) generated working pressure of a hydraulic fluid from a hydraulic system (18) be acted upon, characterized in that the pressure chambers (15a, 15b) of the Schnellhubkolbens (10) during rapid traverse / Tasthub of a em permanently pressurized to high pressure accumulator (34) are fed while the pressure chambers (23a, 23b) of the main piston (20) separated from the hydraulic system and fluid passages (24a to 24f) and bypass channels (26) are connected, so that the hydraulic fluid from the first Pressure chamber (23 a) in the second pressure chamber (23 b) in the stroke direction (BR) of the quick-lift piston (10) is displaced during the rapid traverse almost without pressure. A method according to claim 10, characterized in that the working pressure in the pressure chamber (15b) of the quick-lift piston (10) with the larger effective area of the central control (35) via a pilot-operated check valve (43), a 4/3-way proportional valve (37 ), a controllable proportional valve (39) and a high-pressure accumulator (34) and the working pressure in the pressure chamber (15a) of the quick-lift piston (10) with the smaller effective area via the 4/3-way proportional valve (37) is set. A method according to claim 10, characterized in that the working pressure in the second pressure chamber (23b) of the main piston (2) during the power stroke with the central control (35) via a safety valve (48), at least one pressure sensor (49) for pressure detection, at least one pressure relief valve (46) for limiting the pressure of the flow and a proportional valve (45) for the delivery volume and the hydraulic pump unit (40) and the first pressure chamber (23a) via the tank valve (30) and a collecting tank (44) is adjusted. A method according to claim 10, characterized in that the TDC position of the main piston (20) via a path-measuring system with the central controller (35) is adjusted, wherein the delivery volume of the hydraulic pump unit (40) back regulated before reaching the TDC and with the first pressure chamber (23a) associated with the tank valve (30), a back pressure is generated.

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