EP3209491A1

EP3209491A1 - Press drive device for a press, and press comprising a press drive device

Info

Publication number: EP3209491A1
Application number: EP15775236.1A
Authority: EP
Inventors: Marcus Kosse
Original assignee: L Schuler GmbH
Current assignee: L Schuler GmbH
Priority date: 2014-10-20
Filing date: 2015-10-08
Publication date: 2017-08-30
Also published as: US20170313011A1; WO2016062546A1; US10696000B2; DE102014115241B4; CN107107513A; CN107107513B; DE102014115241A1

Abstract

The invention relates to a press drive device (21) for a press (10), comprising a connecting rod (49) that has an input end (48) and an output end (50). The output end (50) is preferably coupled to a ram (11) via a press gear unit. A drive shaft (35) is mounted so as to be rotatable about a shaft axis W and includes a connecting rod bearing (46) that is eccentric in relation to the shaft axis W. A drive unit (77) comprising a driving motor (30) and a planetary gear set (76) is used for driving the drive shaft (35). For this purpose, a gear output (79) is connected in a rotationally fixed manner to the drive shaft (35), and a gear input (78) is connected in a rotationally fixed manner to a motor shaft (73). The driving motor (30) comprises a rotor (66) that is connected in a rotationally fixed manner to the motor shaft (73) via a rotor hub (67). The rotor (66) is hollow cylindrical and is concentric to the motor shaft (73). This creates mounting space located between the motor shaft (73) and the rotor (66) and designed to arrange a braking device (31) therein.

Description

Press feed device for a press and press with

Press drive device

The invention relates to a press drive device for a press, which serves to drive a plunger of the press. The invention also relates to a press ^having ei ^¬ ne such press drive device.

Press drive devices for driving a press ram are known in many different variants. It has been proposed several times to use electric motors or servomotors in the press drive device. For example, DE 10 2008 034 971 AI describes a press with several direct drive modules, each acting on a pressure point of the plunger. In the direct drive module, a servomotor can be used. The servomotors of various direct drive modules may be either mechanically coupled or electronically synchronized. In electrophotographic ^¬ nical synchronization with four pressure points of the tappet can ge ^¬ rotates about two orthogonal axes or be tilted.

DE 10 2008 063 473 AI proposes a modular buildable press drive. An electric drive motor, for example a servo or a torque motor can be arranged with a gear module at an interface of the press. In addition, a brake may be present in the engine module. The motor can be connected to a corresponding interface on the press via a gear module. Another modular drive system for a press is known from DE 10 2011 113 624 AI. In a drive housing, a crankshaft is mounted via radial bearings. The drive is flanged to the side of the drive housing. At a connecting rod bearing of the crankshaft, a connecting rod is attached, which converts the rotational movement of the crankshaft in an oscillating Be ^¬ movement. A braking device and a Planetenge ^¬ gear can be arranged between the drive and the drive housing. The brake and the drive can also be connected to the transmission on opposite sides. The modular design different Anordnungsmög ^¬ opportunities are created.

In the previous presses, the space required for the press drive device is often considerable. It can therefore be regarded as an object of the present invention to provide a press drive device or a press, which allows a more compact design.

The object is achieved by a press drive device with the features of claim 1 and a press with the features of claim 17.

To the press drive device includes a connecting rod having a drive end and a driven end. The Ab ^¬ drive end is preferably gekop pelt ^¬ a toggle mechanism or through another press gear with the plunger. The press drive device also has a drive shaft, for example a crankshaft or an eccentric shaft. The drive shaft is rotatably mounted about a Wellenach ^¬ se. It has an opposite to the shaft axis eccentrically arranged connecting rod bearing. At the connecting rod bearing the drive end of the connecting rod is mounted. The press drive device has at least one electric drive motor, in particular a torque motor, with a stator and a rotor. A "torque motor" a servo motor is to be understood, which is designed for lower speeds for high torques. The torque motor comprises a high number of pole pairs on. The diam ^¬ ser a torque motor is preferably significantly greater than its axial dimension. The torque motor is required in the axial direction only a small space.

There is at least one drive housing available. Are preferential ^¬, at least a first and a second housing Antriebsge ^¬ present. The number of drive housings can also be greater than two. The first drive housing and the second drive housing are arranged on axially opposite sides of the connecting rod bearing. The drive shaft preferably projects into the first and / or second Antriebsge ^¬ housing.

In one or more of the existing drive housing, a drive motor is arranged, which has a stator and a hollow cylindrical rotor. The housing interior provides a space for the drive motor. Preferably radially within the stator, the rotor is angeord ^¬ net. On its side facing the stator, the rotor can carry permanent magnets.

The rotor is supported by a rotor hub. The rotor is rotatably connected to the rotor hub. The rotor or at least parts thereof and the rotor hub can also be designed integrally oh ^¬ ne seam and joint. The rotor hub as ^¬ umum is rotatably connected to a motor shaft. The Dre- Hung of the rotor by a certain angle of rotation about the Wel ^¬ lenachse thus causes the rotation of the rotor hub and the motor shaft by the same rotation angle.

The press drive device has at least one planetary gear. Each existing drive motor can be assigned a planetary gear. A drive motor and a planetary gear to ^¬ ordered to form a common ^¬ drive unit. Each drive unit can be arranged in a separate drive housing. It is also possible, the planetary gear and the drive motor of a common drive unit anzuord ^¬ nen in two separate drive housings, which are arranged axially adjacent to each other with respect to the shaft axis and interconnected.

The planetary gear has a transmission input and a transmission output. The transmission input is non-rotatably connected to the motor shaft. The transmission output is non-rotatably connected to the drive shaft. The planetary gear has a gear ratio between the transmission input and the transmission output of at least 3, and preferably min ^¬ least 5. The gear ratio is preferably an integer or a decimal number with finitely many decimal places, in particular less than 5 or less than 3 decimal places. As a result, the rotational position or the rotational angle of the drive shaft can be determined very simply and precisely by means of a rotational position or rotational angle determination of the motor shaft by means of a press control without its rotational position having to be detected separately.

Radial between the motor shaft and the rotor and axially be ^¬ adjacent to the rotor hub is an arrangement by the arrangement installation space available, which is set up for arranging a braking device in the respective drive housing.

The inventive construction of the press drive device can be in modular fashion in a drive housing, a drive unit and / or a braking device anord ^¬ NEN. The press drive device can therefore be flexibly adapted to the press. In addition, the space is very small in ^¬ particular in the axial direction parallel to the shaft axis. It is thereby possible to provide a compact press to rea ^¬ taping, wherein the shaft axis of an on ^¬ drive shaft in the direction is oriented at least in the even of the workpiece is transported. The press drive device preferably does not protrude beyond the outer contour of the press frame of the press. Characterized the ENTRANCE ^¬ friendliness to the front and rear of the press for the workpiece transport and / or replacement of the press tool is significantly improved.

The planetary gear has a sun gear, a ring gear, and a plurality of planetary gears disposed between the sun gear and the ring gear and engaged with both the sun gear and the ring gear. The planet gears are preferably rotatably mounted on a common planet carrier. In one embodiment, the transmission ^¬ input is formed by the sun gear. The sun gear is there ^¬ preferably connected directly to the rotationally fixed to the motor shaft and can for example sit directly on the motor shaft. It is also possible to carry out the motor shaft and the sun gear integrally without seam and joint.

The diameter of the motor shaft may be large relative to its axial length along the shaft axis, thereby a high torsional stiffness results. The motor shaft does not act as a torsion spring. For example, the ratio of the diameter may be greater than 0.1 or 0.25 or 0.3 or 0.5 or 0.7 or greater than 1.0. Divided by the length of the door shaft ^¬ Mo The detection of the rotational position of the drive shaft by means of a rotational position ^¬ measurement of the motor shaft is therefore very accurate.

The transmission output may be formed by the planet carrier in one embodiment. The Planetenrad- carrier is rotatably mounted about the shaft axis.

The planet gears can be stored on the fly. Alternatively, it is also possible to support the planet gears on the drive housing and / or on the motor shaft.

In a preferred embodiment of the press drive device, the transmission output is non-rotatably coupled via a coupling device with the drive shaft. The coupling device is in particular designed so that a radial movement is made possible radially to the shaft axis between the drive shaft and the transmission output. In the direction of rotation or in the circumferential direction about the shaft axis, the coupling device provides a non-rotatable and preferably ^¬ free connection between the transmission output and the drive shaft. It is also advantageous if the coupling device also allows an axial relative movement between the transmission output and the drive shaft.

The drive shaft is rotatably supported in one embodiment about single ^¬ Lich two bearing points. The first bearing device and / or the second bearing device are present Preferably formed by rolling bearing devices, but could also be designed as a sliding bearing for pressing with larger pressing or Pleuelkräften.

The drive shaft is rotatably supported in a preferred Ausführungsbei ^¬ game at a first bearing point via a first bearing means and at a second bearing point via a second bearing means. The two bearings are arranged with respect to the connecting rod bearing on axially opposite sides. The first bearing device is arranged between a first bearing part and the drive shaft and the second bearing device is arranged between a second bearing part and the drive shaft.

Preferably, the first bearing means forms a Festla ^¬ ger and the second bearing means a movable bearing. Axial expansions of the drive shaft therefore do not result in stresses in the press drive device. An axial migration of the drive shaft is prevented by the fixed bearing.

Preferably, the first bearing device is present in the region of the coupling device. About the first bearing means of the transmission output and / or the coupling device and / or the drive shaft is supported or mounted on the first bearing part. Preferably, the first bearing ^{¬ device} between the first bearing part and the transmission output or the coupling device is arranged so that the drive shaft is indirectly supported via the first bearing means on the drive housing.

It is preferred if a first drive housing and a second drive housing is present. In particular are the two drive housing arranged on different Axialsei ^¬ th of the connecting rod bearing.

Each drive housing may have a located in the circumferential direction about the shaft axis and / or coaxially to the shaft axis erstre ^¬ ADORABLE peripheral wall. In particular, the stator of a drive motor may be arranged on the inner surface of the circumferential wall assigned to the shaft axis. In addition, at least in each case in the first and the second drive housing in each case an inner wall is present. The inner wall is connected to the peripheral wall on the axial side, which faces the connecting rod bearing and can be referred to as the inner axial side of the first and second drive housing. The drive housing thus has a pot-shaped Ge ^¬ stalt. The inner wall is broken in the region of the shaft axis by ^¬.

It is advantageous if the first bearing part with the first bearing is part of the first drive housing and / or if the second bearing part with the second bearing point is part of the second drive housing. In particular ^¬ sondere the first bearing point on the inner wall of the f ^¬ th driving the housing and the second bearing point on the In ^¬ nenwand of the second drive housing is formed. There, the drive shaft is supported indirectly or directly via the relevant bearing device on the inner wall. In the arrangement, the drive shaft ^¬ ser therefore not pressing on ^¬ rack, but preferably only at the two drive housings is mounted. But it is also possible to store the drive shaft in addition to the press frame, in ^¬ particular in presses with larger pressing forces. The motor shaft is mounted in an advantageous Ausführungsbei ^¬ game of the press drive device to a motor shaft bearing point via a motor shaft bearing device on the drive housing, which interspersed, ^{beispielswei ¬} se on the first drive housing. The motor shaft bearing point is preferably axially adjacent and in particular pos ^¬ lichst arranged close to the transmission input. The motor shaft bearing device can have a larger axial dimension viewed in the axial direction of the shaft axis than the first and / or the second bearing device for supporting the drive shaft. The motor shaft bearing point or the motor ^¬ shaft bearing device is arranged in an embodiment between the transmission input and the drive motor or between the transmission input and the rotor hub. It is advantageous if the installation space for the braking device is located between the motor shaft bearing device and the rotor hub. For this purpose, the rotor hub in ^¬ example connected to the axial end of the rotor, which is remote from the motor shaft bearing device.

The motor shaft and / or the rotor hub and / or the rotor are preferably mounted exclusively on the motor shaft bearing device at the motor shaft bearing point. The rotor and / or the rotor hub are thus indirectly mounted on the drive housing via the motor shaft bearing device via the motor shaft. Viewed from the junction of the rotor hub with the motor shaft of the rotor or the rotor hub is mounted only on one axial side.

In one embodiment, a braking device is present. The braking device is provided to stop the plunger movement in an emergency, for example in case of failure of the electrical power supply. In one or more of the existing drive housing can each be arranged a braking device.

Preferably, the rotor is fixed to the rotor hub at an axial end. For example, in a Antriebsge ^¬ housing both a drive motor and a brake device may be placed. In this case, the braking device can engage axially at least partially in the installation space between the rotor and the shaft axis. Preferably, the braking device is axially adjacent to the rotor hub is arranged ^¬.

In an advantageous Ausfügungsbeispiel the Rotorna ^¬ be a hollow shaft which surrounds the motor shaft. The hollow ^shaft may be non-positively and / or positively connected to the motor shaft in the direction of rotation, ie in the circumferential direction about the shaft axis. From the hollow shaft, spokes or a disk may extend substantially radially or obliquely to the shaft axis, wherein the rotor is supported by the disc or the spokes.

It is advantageous if the first and the second drive ^¬ housing each having a mounting flange for attachment to a press frame. The mounting flange is preferably arranged at a location which is axially spaced from the conrod bearing associated inner axial side or from the transmission output. The attachment ^¬ flange can be designed as an annular flange. The first and the second drive housing is preferably mounted on two opposing plates or cheeks of the press frame such that only the annular flange and the Be ^¬ fastening screws protrude from the space through the two plates or cheeks of the press frame is defi ^¬ ned.

An optional third drive housing may be secured to the attachment flange of the first or second drive housing with a connecting flange. There can be any number at ^¬ drive housing arranged axially side by side and connect to the ^¬ ers th and / or second drive housing in this manner in principle.

In one embodiment, the press drive device does not protrude beyond the outer contour of the press frame. Under the outer contour is a smallest possible cuboid to understand in which the press frame is arranged. By this configuration, a compact design of the press drive device can be achieved. In particular, it is possible, anzuord ^¬ nen the press drive device on or in the press frame, for example in the header of a press. In addition, there is the advantage that the tool change ^{¬ is} simplified, since the area is easily accessible directly from above or behind the press from above and a tool to be changed, for example, via a crane di ^¬ rectly next to the press frame on the press table can be stored ,

High torques can be achieved via the electric drive motor or torque motor. Due to the direct connection of the rotor with the drive shaft high Drehbe ^¬ accelerations or rotational delays of the drive shaft are possible. These are transmitted via the connecting rod and the preferably existing toggle gear on the plunger. So ^¬ accelerations and delays of the plunger are achieved with high amounts. The press drive device or a press equipped with it thus has not only the high energy efficiency but also high dynamics. Full speed of the press drive device is achieved in less than 40 milliseconds in one embodiment. This is due to the fact that the press drive ^¬ device in addition to a low friction and in relation to the torque provided only low moment of inertia.

The rotor and / or the rotor hub and / or other non-rotatably connected to the drive shaft parts can serve by increasing their mass or by attaching at least one flywheel element as a flywheel. The available in the housing interior free space can be exploited to ^{bereitzu ¬} provide such additional flywheel. The additional flywheel must be balanced as ordered to ^¬.

The shaft axis preferably extends in a Tie ^¬ fenrichtung, in which also the workpiece transfer takes place to or from the press.

A press according to the present invention may comprise one or more of the above-described press drive devices. Each press drive device is associated in particular with a toggle mechanism, which is acted on by the connecting rod of the press drive device. If the press has several press drive devices, these are not mechanically coupled to one another. Each press drive device used in the press can control the angle of rotation of the drive shaft and thus the position of the connecting rod or of the respectively connected toggle lever ^gear independently of the other press drive devices to adjust. The press drive devices are coordinated by a press control and speak control ^¬ technically linked.

Advantageous embodiments of the invention will become apparent from the dependent claims, as well as the description. The invention is described below with reference to the attached

Detailed explanation of the drawing. Show it:

1 is a perspective view of an embodiment of a Ausfüh ^¬ tion of a press with two Pres ^¬ senantriebsvorrichtungen,

2 shows the press of FIG. 1 in a front view,

Fig. 3, the press of Figs. 1 and 2 in one

Side View,

Fig. 4, the press according to FIGS. 1-3 in one

Top view,

5 is a sectional partial view of the press according to FIGS. 1-4 in a sectional view ge ^¬ according to the section line VV in Fig. 2 with a drive unit shown schematically,

Fig. 6 is a partial view of the press acc. of the

Fig. 1 to 5 in the sectional view according to the

Section line VI-VI in Fig. 2,

7 shows a press ram and the ram guide of the press according to FIGS. 1 to 6 in per- perspective view, and a schematic ^¬ cal representation of an embodiment of a toggle mechanism of the press,

8 to 11 are each a block diagram of unterschiedli ^¬ cher configurations of a press drive device,

12 is a schematic diagram of a modified embodiment of a toggle mechanism of the press,

Fig. 13 is a schematic schematic representation of a

Bearing arrangement for a toggle mechanism and

Fig. 14 is a schematic diagram of another bearing assembly for a toggle mechanism.

FIGS. 1 to 4 show an embodiment of a ^press 10 in various views. The press 10 has a plunger 11, which is movably guided in a stroke direction H, in particular in the vertical direction, on a press frame 12. To guide the plunger 11, for example, attached to the plunger 11 fixed rollers 15 which abut a respective associated bearing surface 13 of a press frame-side guide member 14 (Fig. 7).

The press frame 12 has a foot part 18 with a Pres ^¬ sentisch 19. On the press table 19, a lower tool can be arranged. With the lower tool, an upper tool can cooperate, which is arranged on the plunger 11. In the press 10 described here, the lower tool is immovably angeord ^¬ net relative to the press frame 12. Only the upper tool can be moved by means of the plunger 11 relative to the press frame and the lower tool. The press 10 may be used for cutting and / or stamping, stamping and / or drawing and / or bending and / or for other forming processes.

The press frame 12 also has a head portion 20. The plunger 11 is located between the head part 20 and the foot part 18. In the embodiment illustrated here, the press 10 is designed as a monoblock press, wherein the foot part 18 and the head part 20 of the Pressenge ^¬ stells 12 are about two in a transverse direction Q with Distance from each other arranged connecting parts or side ^¬ stand connected to each other, each extending from the foot part 18 to the head part 20 in the stroke direction H. In a modification to this, the press 10 could also be designed as a C-frame press or in split design, in which the Pressing elements (header, stand, press table) are connected in a suitable manner.

A depth direction T is oriented at right angles to the stroke direction H and to the transverse direction Q. Viewed in the depth direction T, the press 10 has a front side (FIG. 2) and the front side has a reverse side. In the case of the press 10 illustrated here, the transport of a workpiece from the front or the back to the press 10 or from the press 10 to the front or to the back takes place.

At the head part 20, at least one and in the embodiment described here ^¬ two press drive devices 21 is arranged. The at least one Pressenan ^¬ drive device 21 is used to move the plunger 11 in the stroke direction H.

On the head part 20, the press frame 12 in two depths ^¬ direction T at spaced press frame plates 22nd The press frame plates 22 extend in a plane defined by the transverse direction Q and the stroke direction H. The two press frame plates 22 each have a circular receiving opening 23 for each press drive device 21 (FIG. 5). The receiving openings 23 in the two press frame plates 22 for a common press drive device 21 are arranged in the depth direction T aligned and coaxial about a shaft axis W of the ^¬ press drive device 21.

The press drive device 21 has at least one drive housing. The press drive device 21 according to FIGS. 1-7 has, for example, a first drive housing. se 24 and a second drive housing 25. At the first ^¬ drive housing 24 is arranged a press frames 22 sub-panel 22 and the second drive housing 25 in the other press frame plate in each case coaxially to the same Wel ^¬ lenachse W. The shaft axis W of each Pressenan ^¬ driving device 21 extends in the depth direction T.

Each drive housing 24, 25 has an annularly closed W and Example ^¬ according arranged coaxially to the respective shaft axis W annular circumferential wall in the circumferential direction about the shaft axis 26th The peripheral wall has in ^¬ game according to an axis extending around the shaft axis of circular shape, but could have other shapes. In the embodiment illustrated in FIGS. 1-7, an inner wall 27 is provided which extends substantially radially to the respective shaft axis W. The inner wall 27 of a respective drive housing 24, 25 is located at the axial side on which the drive housing 24, 25 each ^¬ other drive housing is 25 and 24 facing the weils. On the side opposite the inner wall 27, the respective drive housing 24, 25 has a housing opening 33 (FIG. 5) which is closed by a cover 28. In each drive housing 24, 25 thus a substantially cylindrical contoured housing interior 29 is formed. In the housing interior 29, a drive motor 30 and / or a braking device 31 can be arranged.

The first drive housing 24 and the second Antriebsge ^¬ housing 25 has in each case on the inner wall 27 entgegenge ^¬ set axial side a fastening means to the respective drive housing 24, 25 to the associated press frame ^¬ plate 22 to secure. As fastening means, a mounting flange serves at ^¬ game according to at least 32. The loading fixing flange 32 is executed in the illustrated embodiment as an annular flange and surrounds the housing opening 33 of the respective drive housing 24, 25 completely. About holes in the mounting flange 32, the drive housing 24, 25 are bolted to the respective associated press frame plate 22.

Each drive device 21 has a drive shaft 35. The drive shaft 35 is conducted in the embodiment ge ^¬ Mäss of FIGS. 1-7 as an eccentric shaft and can also in a modification thereof by a crankshaft (8-11 Fig.) May be formed.

The drive shaft 35 extends along the shaft axis W and is rotatably supported about the shaft axis W. Various ^¬ dene ways of storage are schematically illustrated in FIGS. 8-11. For supporting the drive shaft 35, a first bearing ^device 37 is provided at a first bearing 36. The first bearing 36 is formed in egg ^¬ ner cylindrical bearing recess 38 of the inner wall 27 of the first drive housing 24. Between the Lageraus ^¬ saving 38 and the drive shaft 35, the first Lagerein ^¬ direction 37 is arranged. The drive shaft 35 is also mounted on a second bearing 39, which is formed, for example, by a bearing recess 38 in the inner wall 27 of the second drive housing 25, by means of a second La ^¬ gereinrichtung 40. The second bearing device 40 is disposed between the bearing recess 38 and the drive shaft 35.

The drive shaft 35 may in one embodiment from ^¬ finally through the first and second bearing means 37, 40 on the first bearing point 36 and the second Lagerstel- le 39 be stored (Fig. 5, 8 and 9). Additional storage ^¬ places are not available.

In the embodiment according to FIGS. 5, 8, 9 and 11 thus form the inner walls 27 with the bearing recesses 38, a first bearing part 41 for the first bearing 36 and a second bearing part 42 for the second bearing 39. In a modification to this embodiment, the 42 may be formed also by a member of the press frame 12 first La ^¬ gerteil 41 and / or the second bearing part (Fig. 10).

At least one of the bearings 36, 39 is designed as a fixed bearing to prevent axial displacement of the drive shaft 35. The respective other bearing point and example ^¬ according to the second bearing 39 and 36 is designed as a floating bearing to avoid tension and constraining forces in the Pres ^¬ senantriebsvorrichtungen 21.

Between the two bearings 36, 39, the drive shaft 35 has a connecting rod bearing 46. The connecting rod bearing 46 is eccentrically arranged ^{¬ to the} shaft axis W. According to the example, the connecting rod bearing 46 sits on an eccentric to the shaft axis W arranged eccentric 47a or a crank pin 47b of the drive shaft 35th

In the embodiment described here, the first and second bearing means 37, 40 are formed by Wälzla ^¬ ger. The connecting rod bearing 46 is also executed in the Ausführungsbei ^¬ game as a rolling bearing.

By means of the connecting rod bearing 46, the drive shaft 35 and, according to the example, the eccentric part 47a or the crank pin 47b is connected to a drive end 48 of a connecting rod 49. The connecting rod 49 of a respective press drive device 21 extends depending on the rotational angle position of the drive shaft 35 approximately in the transverse direction Q or slightly obliquely thereto. At the end opposite the drive end 48, the connecting rod 49 has a driven end 50.

The output end 50 of the connecting rod 49 is coupled in the case of here described ^¬ press 10 with an associated press gear, such as a toggle mechanism 51. It would also be possible to couple the output end of the connecting rod 49 via an eccentric gear or directly with the press ram 11.

Each press drive device 21 is associated, for example, a press gear or toggle 51. The example according to two toggle mechanism 51 are ^{beispielswei ¬} se highly schematically illustrated in Fig. 7. The con ^¬ crete arrangement of a toggle mechanism 51 in the press 10 can be seen from Fig. 6. Each toggle mechanism 51 has a first toggle lever 52 and a second toggle 53. The two toggle levers 52, 53 are articulated to one another via a joint connection 54 and, ^{according to the} example, a knee joint 55. The second toggle 53 is also pivotally connected to a pressure point 56. The first toggle lever 52 is pivotally connected to the press frame 12 at its opposite end to the knee joint 55.

Fig. 12 shows a modified embodiment of the hinge connection 54. The connecting rod 49 has three hinge points, namely one at the drive end 48 (as in Fig. 7), a hinge point 54a for connection to the first toggle 52 and a hinge point 54b for connection to the second Knee lever 53. Incidentally, the toggle mechanism 51 corresponds to the toggle mechanism 51 of FIG. 8.

As can be seen in FIGS. 6 and 13 and in part also in FIG. 3, the knee joint 55 is formed by a knee pivot pin 57 on which the output end 50 of the connecting rod 49 is mounted. The second toggle lever 53 is such as formed by two elbow lever element 53a, 53b, which engage around at one end to the knee pin 57 and are pivotally connected at the other end by means of a first bearing pin 58 with the depending ^¬ weils associated pressure point 56 of the plunger. 11 The two toggle elements 53a, 53b are arranged in the axial direction of the knee joint pin 57 on opposite sides of the output end 50 of the connecting rod 49.

According to the second toggle lever 53 and the first toggle lever 52 by two toggle elements 52a, 52b gebil ^¬ det. The two toggle elements 52a, 52b are arranged on entge ^¬ gengesetzten sides of the knee joint pin 52 so that the output end 50 of the connecting rod 49 and the knee joint 55 associated ends of the two toggle elements 53a, 53b of the second toggle 53 between them befin ^¬ the. Viewed in the depth direction T, the distance between the two toggle lever elements 52a, 52b of the first toggle lever 52 is greater than the distance between the two toggle elements 53a, 53b of the second toggle lever 53. In a modification of the illustrated embodiment, it is also possible, the output end 50 of the connecting rod 49 fork-shaped ^execution . The first toggle lever 52 and / or the second toggle lever 53 may also be with only one Kniehe ^¬ belelement 52a or 52b or 53a or 53b executed. At the opposite end of the knee joint 55, the two toggle elements 52a, 52b of the first toggle lever 52 are pivotally mounted on the press frame 12 via a second pivot pin 59. The second bearing pin 59 is mounted at its two axial ends according to the example in a Lagerausneh- tion of a cheek 60 of the press frame 12. The two cheeks 60 for supporting the second journal 59 in the embodiment in the depth direction T densel ^¬ ben distance as the two press risers 22 (Fig. 1 and 4).

As illustrated in FIGS. 6 and 13, the relatively rotatable elements of the toggle mechanism 51 are mounted via roller bearings. For example, the second La ^¬ gerzapfen 59 is supported via a respective bearing 60 to the cheeks of the press frame 12th The two toggle ^elements 52a, 52b of the first toggle lever 52 are non-rotatably seated on the second pivot pin 59 and are rotatably mounted on the knee pivot pin 57 via a respective rolling bearing. The two toggle elements 53a, 53b of the second toggle lever 53 are non-rotatably mounted on the knee pivot pin 57 and are each rotatably mounted on the second bearing pin 59 via a respective rolling bearing. The second bearing pin 59 is rotatably connected to the plunger 11 at the pressure point 56.

In Fig. 13 it can be seen that the bearings are loaded by the initiation of the pressing force at the pressure point 56 in the stroke direction on its upper side. In an alternative embodiment according to FIG. 14, the loading zone of the bearings is arranged in the lower region. This is achieved in that the bearings, in contrast to the arrangement of FIG. 13 between the toggle lever elements 52a, 52b of the first toggle lever 52 and the second bearing pin 59, between the Knee lever elements 53 a, 53 b of the second toggle lever 53 and the knee joint pin 57, and between the pressure point 56 and the first bearing pin 58 are arranged. The first bearing pin 58 is rotatably connected to the knee lever elements 53 a, 53 b of the second toggle lever 53 and. The knuckle ^¬ steering pin 57 is rotatably connected to the toggle lever elements 52a, 52b of the first bell crank 52 and the second La ^¬ gerzapfen 59 rotatably seated in the cheeks 60 of the Pressenge ^¬ stells 12th

The arrangement of FIG. 14 has the advantage over the arrangement of FIG. 13 has the advantage that all the bearings are located within the Au ^¬ ßenkontur of the press frame or press body. This facilitates the sealing of the press body, in particular ^¬ special for sliding bearings with oil or grease lubrication.

Instead of the example used according to the storage roller bearings and other bearings could in principle be used to ^¬ such as plain bearings. Sliding bearings can be advantageous if larger forces act on the relevant installation parts of the bearing, which can be absorbed only by very expensive bearings.

In the exemplary embodiment, the plunger 11 of the press 10 has two pressure points 56 arranged at a distance in the transverse direction Q. The pressure points 56 are arranged along a straight line extending in the transverse direction Q. The distance between the two pressure points 56 is greater than the dimension of the press table 19 in the transverse direction Q. The two pressure points 56 are therefore not above the press table 19, but in the transverse direction Q considered close to the two side posts of the press frame, the foot part 18 and Connect headboard 20 together. This eliminates one Bending stress of the head part 20 and the press stiffness is increased.

As explained, each press drive device 21 has at least one electric drive motor 30. The at least one drive motor 30 is arranged in the first drive ^housing 24 or in the second drive housing 25. It is also possible to arrange a drive motor 30 in each of the two drive housings 24, 25. In the embodiments according to FIGS. 1 to 10, each press drive ^¬ device 21 to a single drive motor 30.

The drive motor 30 is arranged according to the example in the first drive ^¬ housing 24. It has a stator 65 which is arranged coaxially with the shaft axis W. The stator 65 is fixed to the shaft axis W facing Innenflä ^¬ surface of the peripheral wall 26 at ^¬ play invention.

Radially relative to the shaft axis W, an annular rotor 66 is disposed coaxially about the shaft axis W within the Sta ^¬ tors 65th The rotor 66 carries in Ausführungsbei ^¬ game permanent magnets. The excitation coils are arranged in the stator 65. The drive motor 30 is preferably designed as a ser ^¬ derotor or torque motor. In contrast to servomotors, the torque motor has a high number of pole pairs and is designed for lower speeds and higher torques. Therefore, its diameter compared to its axial size according to example significantly larger.

The rotor 66 of the drive motor 30 is attached to a rotor hub 67 at its axial end associated with the inner wall 27 and the connecting rod bearing 46. The rotor hub 67 has, for example, a radially or obliquely to the shaft axis W extending washer 68 on. The radially inner end of the ^¬ ser disk 68 is connected to a hollow shaft 69 which sits on a motor shaft 73rd The hollow shaft 69 may be connected in the direction of rotation about the shaft axis W positively and / or non-positively with the motor shaft 73. To which the hollow shaft 69 opposite the radially outer end, the rotor hub 67 a holding part 70, on which is fixed Ro ^¬ tor 66th

Instead of the disc 68 could also extend a plurality of spokes between the hollow shaft 69 and the holding part 70.

The rotor hub 67 is preferably made in one piece without seam and joint. The rotor hub 67 and the fact be strengthened ^¬ rotor 66 have a total of a rim-like Ge ^¬ Stalt. Radially inside the rotor 66 and axially adjacent to the disc 68 and the rotor hub 67 remains a space or receiving space 71. In this receiving space 71 is sufficient space when in addition to a drive motor 30, a braking device 31 is to be arranged in a drive housing.

The rotor 66 is rotatably connected via the rotor hub 67 with the Mo ^¬ torwelle 73. A rotation of the rotor 66 by a predetermined angle of rotation about the shaft axis W thus leads to the rotation of the motor shaft 73 by the same rotation angle. The immediate non-rotatable mechanical connection between the rotor 66 and the motor shaft 73 is ^spiels free ^¬ example.

On at least one drive housing 24, 25 and beispielsge ^¬ according to the first drive housing 24, a sensor 72 is angeord ^¬ net. The sensor 72 sits example according to extension of Motor shaft 73 and is penetrated by the shaft axis W. The sensor housing is located inside (Fig. 5) or au ^¬ ßerhalb of the housing interior 29 (Fig. 8 to 11) and, for example, at which the first drive housing 24 ver ^¬ closing lid 28 is disposed to be. The sensor 72 is used to detect the rotational position of the drive motor 30. The rotation ^¬ position detection can be done touching or non-contact. Each drive motor 30 or each motor shaft 73 is preferably associated with at least one sensor 72.

If several drive motors 30 connected to a common motor shaft 73, the rotational position both on ^¬ drive motors 30 can be determined by a common sensor 72nd The drive motors 30 are mounted in matching rotational positions.

Each drive motor 30 is a planetary gear 76 zugeord ^¬ net, so that in each case a drive motor 30 and a planetary gear 76 form a drive unit 77. The Planetenge ^¬ gear is arranged in a space between the motor shaft 73 and the drive shaft 35 coaxial with the shaft axis W ^¬ . A transmission input 78 of the planetary gear is rotatably connected to the motor shaft 73. A Getriebeaus ^¬ gear 79 is rotatably coupled to the drive shaft 35. The coupling device 80 allows a relative movement between the gear output 79 and the drive shaft 35 radially to Wel ^¬ lenachse W. In addition, the coupling device 80 also allow an axial relative movement along the shaft axis W. In the direction of rotation or circumferential direction about the shaft axis W, the coupling device 80 generates a non-rotatable and preferably backlash-free coupling. The Kopp ^¬ ment can be done non-positively and / or positively.

In the exemplary embodiments illustrated in FIGS. 5 and 8-11, the first bearing 36 is arranged in the region of the gearbox output 79 or the coupling device 80. The drive shaft 35 is mounted or supported indirectly via the Kopp ^¬ treatment device 80 and / or the transmission output 79 on the first drive housing 24.

The planetary gear 76 has a sun gear 81, a ring gear 82 disposed coaxially around the sun gear 81, and a plurality of planet gears 83 engaged with both outer teeth of the sun gear 81 and inner teeth of the ring gear 82. The ring gear 82 is secured in the Ge ^¬ häuseinnenraum 29 of the first drive housing 24, for example on the peripheral wall 26th

The sun gear 81 forms the transmission input 78. It is preferably located directly rotationally fixed manner on the motor shaft 73 or may be formed integrally without seam and joint with the motor shaft ^¬ 73rd Upon rotation of the motor shaft 73, the sun gear 81 rotates at the same angle of rotation and drives the planetary gears 83, which zen in the ring gear 82 abwäl.

The planet gears 83 are rotatably mounted on a Planetenradträ- ger 84 of the planetary gear 76. The Planetenrad- carrier 84 is rotatably connected to the transmission output 79 and forms the transmission output 79. As the transmission output 79 can also serve an output shaft, which is rotatably connected to the planet carrier 84. The planetary gears 83 may be cantilevered or, as illustrated only in dotted lines in FIG. 8, be supported by a support unit 89 on the first transmission housing 24 radially to the shaft axis W.

The drive unit 77 can be arranged in a common drive housing ^¬ example, according to the first drive housing 24 and / or the second drive housing 25 (Fig. 5 and 9-11). Alternatively, it is also possible to arrange the planetary gear 76 and the drive motor 30 of a drive ^¬ unit 77 in two separate drive housings. By way of example schematically is illustrated in Fig. 8 that the planetary gear 76 is disposed in the first drive housing 24 and the associated drive motor 30 of the drive unit 77 in a third drive housing 87, where ^¬ in the third drive housing 87 via a coaxial with the shaft axis W arranged connecting flange 88 with can be connected to the mounting flange 32. It is understood that other connection possibilities between two axially adjacent drive housings 24, 87 can be used.

The sensor 72 for detecting the rotational position of the motor shaft 73 can also be used to determine the plunger position. Based on the rotational position of the motor shaft 73 can be determined by means of the known gear ratio, the rotational position of the drive shaft 35 and therefore the plunger position. It is particularly advantageous if the Übersetzungsver ^¬ ratio of the planetary gear 76 from the transmission input 78 to the transmission output 79 is an integer or a decimal number with a finite number of decimal places, for example 3 to 5 decimal places to allow an exact calculation. Alternatively, it is also possible to provide a further sensor 72, which detects the rotational position of the drive shaft 35. This additional sensor 72 for detecting the rotational position of the drive shaft 35 is optional.

The braking device 31 is arranged in the embodiments according to FIGS. 1 to 8 and 11 in the second drive housing 25. Alternatively or additionally, a braking device 31 may also be present in the first drive housing 24 (FIGS. 9, 10 and 11). Is in the drive housing 24, 25 also includes a drive unit 77 provided, remains in the receiving space 71 space for arrangement of the braking means 31. A brake part is fixedly connected to the second Antriebsgehäu ^¬ se 25 and, for example in accordance with the inner wall 27, currency ^¬ end of the other brake member rotationally fixed to the drive shaft 35 is connected. On the inside of the inner wall 27, for example, corresponding fastening means for the braking device 31 and the housing-fixed part are present. If there is an emergency situation, such as a failure of the electrical power supply for the press drive device 21, the braking device is initiated 31, and stops the rotation of the drive shaft 35 and thus the oscillating movement of the plunger 11. Each An ^¬ drive device 21 has at least one braking device 31.

The press 10 has no hydraulic Überlastsi ^¬ insurance. The overload protection is by an electrical or electronic control of at least one

electric drive motor 30 of each press drive device 21 executed. The electric drive motors 30 of different press drive devices 21 are not mechanically positively coupled with each other. The coordinated rotating the electri ^¬ rule drive motors 30 different press drive devices 21 are made for the respective associated shaft axis W by the press control. Thus, there is a coordination of the rotational movements of the drive motors 30 different press drive devices 21 by control engineering or control engineering measures.

Because the press drive devices 21 are not mechanically positively coupled, a different position of the relevant pressure point 56 in the stroke direction H can be preset via each press drive device 21. In order to avoid damage to the guidance of the plunger 11, the guide allows the plunger 11 in addition to the movement in the stroke direction H at least one further degree of freedom of movement, namely an inclination with respect to a plane which is spanned by the depth direction T and the transverse direction Q. The inclination is, for example, ei ^¬ ne tilting movement about an axis parallel to the depth direction T.

If pressure points 56 arranged at a distance from one another are additionally provided in the depth direction T in a modified exemplary embodiment, a tilting movement about an axis which is aligned parallel to the transverse direction Q can additionally be permitted. In the exemplary embodiment illustrated here, the plunger 11 is supported at twelve points via a respective roller 15 with respect to a contact surface 13 (FIG. 7). Four contact surfaces 13 have either a normal vector in the depth direction T and four contact surfaces have a normal vector in the transverse direction Q. The rollers 15 are in the stroke direction in two of spaced elevations arranged on the plunger 11. In the one altitude, for example, the lower Höhenla ^¬ ge, is located at each of the eight contact surfaces 13, a roller 15 at. In the other altitude, according to the example of the upper Hö ^¬ henlage, is only at the four contact surfaces 13 ei ^¬ ne role 15, the normal vector in the depth direction T shows. This allows tilting of the plunger 11 about an axis parallel to the depth direction T. In the same way could alternatively be realized tilting about an axis parallel to the transverse direction Q, if in the other altitude, for example, the upper altitude, the rollers 15 only at the four contact surfaces 13 each have a role whose normal vector in the transverse direction Q shows. If the rollers 15 are arranged only at an altitude, tilting of the plunger 11 about axes in two spatial directions T, Q is possible.

To determine the force applied by the plunger 11 pressing force, the press 10, not shown force sensors. The force sensors may be arranged at any point in the drive train between the drive motor and the plunger 11. For example, a force sensor may be provided for determining the press force at each gear Kniehebelge ^¬ 51st The sensor signal of the force sensor is transmitted to the control of the press 10 and evaluated. To avoid an overload is detected depending on the current rotational position, and therefore dependent on the current position of the plunger 11 and dependent on the sensor signal of the Krafts ^¬ sensor whether an overload and thus a Beschädi ^¬ supply of the press 10, the tool or the workpiece is imminent. In this case, the at least one Antriebsmo ^¬ gate 30 may be supplied with current or vice ^¬ switched into a generator mode, that a braking force against the aktuel- len rotation direction and the plunger movement is stopped. Such an overload function can also be carried out by control engineering or control measures without the use of hydraulic overload devices.

If a press drive device 21 has a plurality of drive motors 30, then the drive torque and / or the nominal force travel can thereby be increased. Preferably ^¬ which the existing drive motors 30 a common press drive device 21 is driven independently, for example, separate frequency converter, by a press control. Is not required, the torque of all the drive motors 30 at a forming task or during the ram movement does not need the torque of all At ^¬ drive motors 30 at least in a portion of the motion profile, so one or more of the drive motors are operated, for example, normally passively or in the generator mode. It is also possible to control the drive motors 30 such that overall the losses of all the drive motors 30 are minimized. The actuation of the existing drive motors 30 is carried out such that the required torque is provided by the drive motor ^¬ ren 30 so that a ho possible ^¬ her overall efficiency results. In order to have greater variability, drive motors 30 with different torque-current characteristics and / or different efficiency maps can also be used.

In the generator mode, for example, energy can be fed back into an electrical intermediate circuit into energy ^¬ memory. This energy can be at the next working stroke be used. The network load can be reduced thereby.

Depending on the forming task, the press ram 11 can be moved with any movement profile in the stroke direction H. For example, the press ram 11 can be stopped at bottom dead center. For oscillating movement of the press ram 11 to the at least one ^¬ drive motor at the top dead center and the bottom dead center of the slide movement can reverse its direction of rotation and therefore are driven in a rotational angle range pendulum. It is also possible to select the rotation angle range symmetrically or asymmetrically about the bottom dead center, so that after each direction of rotation reversal of the at least one drive motor 30, the bottom dead center of the plunger movement is traversed. The at least one drive motor 30 may also be driven about the shaft axis to W ^¬ without direction reversal rotation. Thus, a ram movement can take place according to the following principles:

- tied away, like a classic flywheel press or

- strong, like a hydraulic press or

- energy-bound, as in a forging ^press with egg ^¬ ner spindle or on the hammer principle.

Different configurations of a press drive device 21 are illustrated in FIGS. 8 to 11. As already explained, shows the configuration of FIG. 8, a first drive housing 84 with a planetary gear 76, an associated third drive housing 87 to the drive motor 30 of the drive unit 77 and a second at ^¬ drive housing 25 31, with a braking device, the second Drive housing 25 is disposed opposite to the connecting rod bearing 46 on the axially opposite side.

The embodiment of FIG. 9 corresponds Wesentli ^¬ chen the configuration of Fig. 8. The difference is that the second drive housing 25 here serves only for providing the second bearing point 39 to the second storage device 40. The braking device 31 is arranged between the planetary gear 76 and the drive motor 30 of the drive unit 77. In order to enable this, the rotor hub 67 is connected with the axially facing the planet gear from ^¬ end of the rotor 66th Thereby, a sufficiently large receiving space 71 is provided radially inward of the rotor 66 around the motor shaft 73 in which the braking device 31 is disposed.

A further difference of the embodiment according to FIG. 9 compared to the embodiment according to FIG. 8 is that the drive unit 77 is arranged completely in the first drive ^housing 24. Since a large installation space is available in the second drive housing 25, a sensor 72, which detects the rotational position of the drive shaft 35, can be arranged within the second drive housing 25.

In the embodiment schematically illustrated in Fig. 10, only the first drive housing 24 is present. The first drive housing 24 is in this embodiment completely outside the space between the two Pressenge ^¬ partition walls 22 of the press frame 12 is arranged. The Be ^¬ fastening flange 32 of the first drive housing 24 is arranged here on the press frame 12 associated axial side. The second bearing 39 and the second La ^¬ gereinrichtung 40 is between the drive shaft 35 and the Press frame 12 and the press frame wall 22 vorgese ^¬ hen. In addition, on the first drive housing 24 adjacent press frame wall 22, a further, third La ^¬ gerstelle 90 may be provided with a third bearing means 91.

In the example illustrated in Fig. 11 embodiment, the arrangement of the drive unit 77 and the brake ^¬ device 31 corresponds to the first drive housing 24 of the configura ^¬ tion of FIG. 10. The arrangement of the drive unit 77 and the braking device 31 in the second drive housing 25 is here similar to the the first drive housing 24. The first bearing 36 is provided on the first drive housing 24 and the second bearing 39 on the second drive housing 25. Analogously to the third bearing point 90 is adjacent immediacy ^¬ bar to the second bearing point 39, a fourth La ^¬ gerst elle 92 is provided with a fourth bearing device 93rd

The proposed in Figures 10 and 11 further storage devices 91, 93 may be useful when the connecting rod 49 large forces acting on the drive shaft 35, which can be better supported against the press frame 12 than against a drive housing 24, 25. Otherwise could at accounts for the embodiments according to FIGS. 10 and 11 also, optionally, the third bearing point 90 and / or the fourth bearing ^¬ location 92.

As can be seen in FIGS. 8-11 further, a Mo ^¬ torwellen-bearing device 97 for supporting the motor shaft 73 is present. The motor shaft bearing device 97 is in a support wall 98 of the first drive housing 24 and in the embodiment of FIG. 11 in the second drive housing 25 is provided. The support wall 98 is adjacent to the transmission input 78 and arranged, an axial wall from ^¬ circuit form (Fig. 8) or as an intermediate wall in the perception ^¬ ren of the drive housing 24 or 25 carried out (FIG. 9-11).

In the exemplary embodiments described here, the motor shaft 73 is mounted on the support wall 98 exclusively via the motor shaft bearing device 97. On the motor shaft bearing means 97, the rotor hub 67 and / or the rotor 66 is rotatably mounted, beispielsge ^¬ Mäss further bearing means for the rotor 66 and / or the rotor hub 67 are not provided at additional bearing locations. Starting from the rotor 66 or the rotor hub 67, the bearing of the motor shaft 73 together with the rotor hub 67 and the rotor 66 takes place axially only on one side of the drive motor 30 or the rotor hub 67.

In all embodiments of the press drive device 21, in principle, an external rotor motor could be used instead of the Innenläu- used according to the example, but this is less advantageous for the compact arrangement in the drive housing.

In all embodiments of the press drive device 21, the rotor and / or the rotor hub and / or other non-rotatably connected to the drive shaft 35 parts by increasing their mass and / or by attaching at least one flywheel element 99 serve as a flywheel (Fig. 11). The available space in the housing 29 free space can be exploited to provide such additional ^¬ flywheel. The invention relates to a press drive ^device 21 for a press 10 with a connecting rod 49, which has a drive ^¬ de 48 and a driven end 50. The output end 50 is preferably coupled via a press gear with a plunger 11. A drive shaft 35 is rotatably mounted about a shaft axis W and has an eccentric with respect to the shaft axis W arranged connecting rod bearing 46. An on ^¬ drive unit 77 with a drive motor 30 and a Pla ^¬ Netengetriebe 76 serves to drive the drive shaft 35. For this purpose, a transmission output 79 is rotationally fixed with the drive shaft 35 and a transmission input 78 rotatably connected to egg ^¬ ner motor shaft 73. The drive motor 30 has a rotor 66 which is rotatably connected via a rotor hub 67 with the motor shaft 73. The rotor 66 is designed as a hollow cylinder and arranged concentrically with the motor shaft 73. Thereby, an installation space is provided between the motor shaft 73 and the rotor 66, which is provided and arranged for arranging a braking device 31.

Reference sign list: Reference sign list:

10 press

11 pestles

12 press frame

13 contact surface

14 guide element

15 roll

18 foot part

19 press table

20 headboard

21 press drive device

22 press riser

23 receiving opening

24 first drive housing

25 second drive housing 26 peripheral wall

27 inside wall

28 lids

29 housing interior

30 drive motor

31 braking device

32 mounting flange

33 housing opening

35 drive shaft

36 first depository

37 first storage facility

38 bearing recess second depository

second storage facility

first bearing part

Second bearing part connecting rod bearing

a Exzenterteil

b crank pin

drive end

pleuel

output end

Toggle mechanism

first toggle

a toggle element of the first knee lever b toggle element of the first toggle lever second toggle lever

a Knee lever element of the second knee lever B Knee lever element of the second knee lever Articulated connection

a pivot point

b pivot point

knee

pressure point

knee pin

first journal

second journal

Cheek stator

rotor

rotor hub

disc 69 hollow shaft

0 holding part

71 recording room

72 sensor

73 Motor shaft

76 planetary gear

77 Drive unit

78 transmission input

79 Transmission output

80 coupling device

81 sun wheel

82 ring gear

83 planetary gear

84 planet carrier

87 third drive housing

88 connecting flange

89 support unit

90 third depository

91 third storage facility

92 fourth depository

93 fourth storage facility

97 Motor shaft bearing device

98 retaining wall

99 flywheel element

H stroke direction

Q transverse direction

T depth direction

W shaft axis

Claims

Claims:

A press drive device (21) for a press (10), comprising a connecting rod (49) having a drive end (48) and an output end (50), having a drive shaft (35) rotatable about a shaft axis (W) and a connecting rod bearing (46) arranged eccentrically with respect to the shaft axis (W), on which the drive end (48) of the connecting rod (49) is mounted, with at least one drive housing (24, 25) extending circumferentially around the shaft axis ( W) and / or coaxially to the shaft axis (W) extending peripheral wall (26), wherein at least one of the existing drive housing (24, 25) a drive motor (30) is arranged, the egg ^¬ nen stator (65) and a hollow cylindrical rotor (66), with a rotor hub (67) which is non-rotatably connected to a motor shaft ^¬ (73) and to which the rotor (66) be ^¬ consolidates, with at least one planetary gear (76), the one with the motor shaft (73) rotatably connected gear ^¬ input (78) and one with the Ant input shaft (35) rotationally fixed to output transmission ^¬ (79) and which in one of the drive housing (24, 25) is arranged, wherein radially between the motor shaft (73) and the rotor (66) and axially adjacent to the rotor hub (67) a receiving space (71) is provided, which for arranging a braking device (31) in the respective Antriebsgehäu ^¬ se (24, 25) is set up.

Press drive device according to claim 1,

is characterized in that the transmission input (78) by a sun gear (81) of the planetary gear (76) forms ^¬ ge.

Press drive device according to claim 2,

characterized in that the sun gear (81) is unmit ^¬ immediacy rotatably connected to the motor shaft (73).

Press drive device according to one of the preceding claims,

characterized in that the transmission output (79) by a planet carrier (84) of the planetary gear (76) is formed.

Press drive device according to one of the preceding claims,

characterized in that the transmission output (79) via a coupling device (80) rotatably coupled to the drive shaft (35), wherein the coupling ^{¬ device} (80) has a relative movement radially to the shaft axis (W) between the drive shaft (35) and the transmission output (79).

Press drive device according to one of the preceding claims,

characterized in that at a first storage location le (36) a first bearing device (37) is present, which supports the drive shaft (35) on a first bearing part (41) and in that a second bearing device (40) is provided at a second bearing point (39), which drives the drive shaft (35 ) on a second bearing part (42) superimposed, wherein the two bearing points (36, 39) on axi ^¬ al different sides of the connecting rod bearing (46) angeord ^¬ net are.

7. Press drive device according to claim 6,

characterized in that the first bearing part (41) with the first bearing point (36) is part of a ers ^¬ th driving housing (24) and / or that the second bearing part (42) with the second bearing point (39) Be ^¬ component of a second drive housing (25).

8. Press drive device according to claim 6 or 7,

characterized in that the first bearing means (37) or the second bearing means (40) forms a fixed bearing and the respective other bearing means (40 or 37) forms a floating bearing.

9. Press drive device according to one of the preceding claims,

characterized in that in each case a Planetenge ^¬ gear (76) and a drive motor (30) form a drive ^¬ unit (77) which is arranged in a common drive housing (24, 25).

10. Press drive device according to claim 9,

characterized in that the motor shaft (73) via a motor shaft bearing means (97) on the drive housing (24, 25) is mounted.

11. Press drive device according to claim 10, characterized in that the motor shaft bearing device (97) axially adjacent to the transmission input (78) is arranged.

12. Press drive device according to claim 10 or 11, characterized in that the receiving space (71) for the braking device (31) axially between the motor shaft bearing means (97) and the rotor hub (67).

13. Press drive device according to one of the preceding claims,

characterized in that the rotor hub (67) has a radially extending to the shaft axis (W) extending washer (68) or radially to the shaft axis (W) extending spokes on which the rotor (66) is attached.

14. Press drive device according to one of the preceding claims,

characterized in that the rotor hub (67) has a hollow shaft (69) which closes the drive shaft (35) ^¬ and rotatably ver ^¬ connected with the drive shaft (35).

15. Press drive device according to one of the preceding claims,

characterized in that in at least one of the existing drive housing (25) a braking device (31) is arranged.

16. Press drive device according to one of the preceding claims,

characterized in that in at least one of the existing drive housing (24, 25, 87) both a drive motor (30) and a braking device (31) is arranged and the braking device is arranged axially adjacent to the rotor hub (67) and at least partially into the room between the rotor and the shaft axis (W) engages.

17. Press (10) with a press frame (12) on which a plunger (11) is movably guided in a stroke direction (H), with at least one toggle mechanism (51), the first toggle lever (52) and a second toggle lever (53) interconnected by a hinge connection (54), said first toggle lever (52) hinged to said press frame (12) and said second toggle lever (53) articulated to said plunger (11) at a pressure point (56). is connected, and with at least one press drive device (21) according to one of the preceding claims, wherein the output end (50) of the connecting rod (49) with the Gelenkver ^¬ bond (54) is connected.

18. Press according to claim 17,

characterized in that two press drive devices (21) are present, the movement with pestle (11) via a respective toggle mechanism (51) pelt ^¬ pelt. Press according to claim 17 or 18,

characterized in that a first and / or a second drive housing (24, 25) of each press drive (21) provides a housing interior (29) in which a drive motor (30) and / or a braking device (31) is arranged, wherein the housing interior (29) within the outer contour of the press frame (12) is arranged on ^¬ .