Die-side ejector device for workpieces in single-stage or multi-stage presses

Abstract

In a die-side ejector device for presses, a stationary press die cooperates with a press ram on a press frame in order to shape a blank introduced into a bore of the press die. An ejector pin is displaceably provided in a bore in the press frame, said ejector pin being biased against an ejector lever which is pivotable by an actuator lever between a starting position and a final ejection position and which is supported, on its side facing away from the ejector pin in its starting position, on a pressure piece on the press frame.

Description

[0001] This application claims priority to German application DE, 102 13 850.8 filed Mar. 27, 2002. Said application is incorporated by reference herein.

BACKGROUND OF THE INVENTION

[0002] The invention relates presses and more particularly presses with to a die-side ejector devices for workpieces in single-stage or multi-stage presses, wherein a stationary press die is provided on a press frame, said press die cooperating with a press ram for shaping a blank introduced into a bore of the press die, said device comprising an ejector pin slidably supported within a bore in the press frame, the die-side end of said ejector pin protruding into the bore of the press die and the other end thereof being biased against an ejector lever which is in turn pivotable, via an actuating lever driven by a cam gear, between a starting position, in which the die-side end of the ejector pin is retracted into the bore of the die, and a final ejection position, said ejector lever having its side facing away from the ejector pin in its starting position supported on a pressure piece mounted on the press frame.

[0003] Such die-side ejectors are used in order to eject workpieces, such as screws, bolts, rivets or similar parts, again from the die in single-stage or multi-stage presses after the shaping operation, said ejection operation being integrated in the cycle of press operation.

[0004] Devices for generating a die-side ejection movement after the pressing operation in order to eject workpieces from dies on automatic shaping presses have been known for a long time, in which devices the workpiece is introduced in the shape of a wire or bar and contacts the movable plunger of an ejector device, which plunger supports the blank during the shaping operation and then ejects it from the die. In addition to the function that the ejector pin has to be capable of supporting and absorbing the forces exerted during the shaping of the workpiece, it should also be adjustable in its starting position retracted into the die in order to allow adjustment to different workpieces.

[0005] What all known solutions have in common is that the ejector systems often provided with many joints, levers, etc. have a considerable mass and, in some cases, require considerable idle strokes for adjustment as well as additionally exhibit considerable bearing clearances, which in turn leads to inaccuracy and considerable wear of these structural elements. Such ejector device is described, for example, in DE 16 27 977 B2.

[0006] EP 0,950,447 A2 discloses a device for die-side ejection of workpieces in forging presses which also uses a considerably large number of joints, levers etc. and thus a large number of masses. If, in this case, the fixed point of the ejector pin retracted into the die is to be adjusted, a double adjustment needs to be performed, namely an adjustment of the stroke and an adjustment of the starting point of the ejector pin. Such solution is not only very expensive, but also complicated and cumbersome in terms of adjustment to a different workpiece.

[0007] A simpler solution than this, wherein only one setting needs to be changed for such adjustment (so-called “one-point solution”), is known from U.S. Pat. No. 3,266,071. In this known construction, the ejector lever is supported, on its side opposite the ejector pin, on an actuator lever which is driven by a cam gear and, during the pivotal movement thus initiated, correspondingly causes the ejector lever to move the ejector pin. The actuator lever is in turn pivotable, at one end thereof, about an axle mounted on an adjusting screw screwed into the press frame. In this known solution, the ejector lever is supported, in its starting position (when the ejector pin is retracted into the die), on the end of the actuator lever, at which end said lever is arranged on the adjusting screw, so that the force exerted on the workpiece during the shaping operation and exerted on the ejector lever, via said workpiece, is transferred from said ejector lever to the adjusting screw via the actuator lever and is supported by the press frame. The supporting force is thus introduced into the supporting block or the press frame via a screw thread, which is also not advantageous. If an adjustment of the retracted fixing point of the ejector pin is to be effected, this requires rotation of the adjusting screw, which is also time-consuming and somewhat cumbersome.

[0008] Moreover, adjustment of this known construction toward a small stroke of the ejector lever results in a relatively large idle stroke. The proportionality of the cam gear is then no longer guaranteed.

[0009] A device of the above-mentioned type is known from DE 851,792 C. In this case, the ejector lever is in turn supported, at its lever end facing away from the ejector pin, on an adjusting screw screwed into the press frame. Thus, while the shaping force exerted during the shaping operation is transferred to the adjusting screw via the ejector pin and the ejector lever without interposition of an actuator lever and, thus, to the press housing, in this case the supporting force, however, has to be introduced into the supporting block via a screw thread. Moreover, the corresponding end of the ejector lever, on one side of which the ejector pin acts and the other side of which contacts the adjusting screw, is fork-shaped, with the sides of the fork ends facing the corresponding contacting surfaces being rounded off. Thus, the transfer of the supporting forces is effected via individual, spaced apart, relatively small supporting surfaces, which leads to stress peaks in the material of the ejector lever and thus also to increased wear. Moreover, this known device uses an extremely complicated arrangement comprising many joints and levers, in turn requiring considerable masses to be moved. Also, adjustment of the starting position of the ejector pin in its position retracted into the press die via the adjusting screw is cumbersome, especially because it simultaneously also leads to a certain change in the position of the lever mechanism arranged subsequently of the ejector lever.

[0010] In view thereof, it is an object of the invention to improve a die-side ejector device of the aforementioned type in such a manner that it allows particularly efficient introduction of the forces exerted on the ejector lever during the shaping operation into the press frame and also quick and easy adjustment of the starting position of the ejector pin retracted into the die.

SUMMARY OF THE INVENTION

[0011] According to preferred embodiments of the invention, this is achieved, in a die-side ejector device of the aforementioned type, in that the ejector lever is pivotably arranged on a carrier part, which is displaceable on the press frame, in a direction perpendicular to the longitudinal axis of the ejector pin and in parallel with the plane of pivot of the actuator lever, between two stops and which is provided, on its side facing the pressure piece, with a shaped surface for contact therewith, said shaped surface being designed for areal contact with a complementary shaped surface on the pressure piece, wherein both shaped surfaces maintain their areal, complementary contact in the starting position of the ejector lever even when the carrier part is being displaced.

[0012] In the solution according to preferred embodiments of the invention, too, the forces to be absorbed do not initially act on the gear for ejection, wherein the pressing force may not be absorbed directly via the pressure piece forming a fixed stop in the press frame or a corresponding pressure plate provided on said frame. The device according to the invention has a considerably smaller mass than the known devices, and the pressing force produced can be introduced directly into the press frame without being supported, as in some prior art references, on the drive for the ejector lever. Adjustment of the retracted starting position of the ejector pin may be effected simply by a corresponding displacement of the carrier part between its two displacement stops, wherein, in the end position of the end of the ejector lever retracted into the die, the head of said lever is always supported via the complementary contacting surfaces of the pressure piece and of the ejector lever by areal contact (and thus over a relatively large surface area) on the frame. Due to the fact that, even when the carrier part is being displaced, both shaped surfaces maintain their areal, complementary contact, said areal support on the pressure piece is always equally achieved even upon a change of the retracted position of the ejector pin. In doing so, the supporting surface of the ejector lever on the press frame (according to the invention: via the pressure piece), in turn, need not be changed even upon a change in the retracted starting position of the ejector lever, but said support is always effected on the pressure piece, which itself is not positionally shiftable, or in other words: Movements always begin and end at the same location, regardless of the setting selected for the device according to the invention. On the whole, the invention has a very compact design comprising relatively few levers and, thus, small masses. In this case, adjustment of the carrier part can be effected in any suitable manner, e.g. also by servomotor control, so that a servomotor-controlled adjustment or setting of the ejection stroke may optionally be effected even during operation of the shaping machine. Thus, also the front ejection position of the ejector plunger always remains the same.

[0013] The shaped surfaces complementing each other on the ejector lever, on the one hand, and on the pressure piece, on the other hand, may be realized in any shape which ensures that both shaped surfaces maintain their areal, complementary contact even when the carrier part is being displaced. Particularly preferably, this may be achieved if an ejector device according to the invention, for example, the shaped surface on the ejector lever, corresponds to a curved cam extending in the shape of a cylinder segment and if the complementary counter-shaped surface, which also extends in the shape of a cylinder segment, is provided on a pressure piece which otherwise has a cylindrical shape. In a simple manner, a very effective design of the shaped surfaces is thus realized, said design ensuring the desired areal, complementary contact in any position of the carrier piece.

[0014] Particularly preferably, the pressure piece is pivotable about a central axis and, preferably again, is provided on a pressure plate mounted on the press frame.

[0015] The design of the carrier part in an ejector device according to the invention may also be realized in any suitable form, for example, as a slidable supporting carriage or as a movable supporting pusher.

[0016] Displacement of the carrier part is also realizable in any suitable manner, which may be both by a motor-controlled worm drive and, particularly preferably, via a servomotor drive.

[0017] Particularly preferably, the ejector lever according to the invention is realized as a two-armed lever, said ejector pin contacting the end region of one lever arm and a rotatable roll being mounted on the end region of the other lever arm, said roll being pressure-biased against the actuator lever, which actuator lever, viewed relative to the ejector lever, is provided on the same side of the ejector lever as the ejector pin. In this manner, an ejector device having a particularly compact design and comprising few individual parts is realized, which functions in an excellent manner.

[0018] Also, according to a further preferred embodiment of the invention, the cam gear for the actuator lever comprises a cam disk (cam plate) mounted on an ejector shaft, on which cam disk there runs a roll rotatably mounted on the free end of the actuator lever, said actuator lever being biased against the cam disk in order to urge the roll against the cam disk. This also allows to achieve a very simple, but still excellently functional design of the cam gear employed, comprising few levers and, thus, small masses.

[0019] In the ejector device according to the invention, the ejector pin is preferably formed by a portion provided as a displaceable piston inside the bore in the press frame and by a subsequent smaller-diameter portion protruding into the bore of the press die, said latter portion passing through a cover plate which closes the bore in the press frame on the die side, with the region between the piston portion and the cover plate of the bore in the press frame being connected to a pressure air supply line in order to bias the ejector pin against the actuator lever. The pressure air supply line ensures the desired bias of the ejector pin against the ejector lever, while the applied pressure air, due to its compressibility, simultaneously also allows suddenly appearing pressure peaks to be cushioned.

[0020] In the ejector device according to the invention, use is particularly preferably made also of a device for biasing the ejector lever in a direction toward the actuator lever, said device being independent of the actuator pin, so that the roll at the end of the actuator lever is always pressed against the cam disk on the ejector shaft with a certain compressive bias. This is particularly advantageously realized such that the independent device consists of a piston which is spring-biased against the ejector lever and is arranged in a further bore in the press frame, said piston being supported on the side of the ejector lever facing it, via a sliding shoe.

[0021] Advantageously, the ejector pin is likewise supported on the ejector lever via a suitable sliding shoe which, in a manner known per se, encompasses a ball-shaped end of the ejector pin with a complementary receiving shape and is pivotable relative thereto, at least to a certain extent.

[0022] Both sliding shoes preferably run on a lateral surface of the ejector lever which is, on the whole, provided as a planar surface, on which the sliding shoes can slide also upon adjustment of the carrier part.

[0023] The invention shall be explained in more detail below, essentially by way of example and with reference to the Figures.

DESCRIPTION OF THE FIGURES

[0024] FIG. 1 shows a schematic view, in partial section, of a device according to the invention comprising an ejector lever and an ejector plunger in a first setting for ejection of a short workpiece;

[0025] FIG. 2 shows a view, similar to that of FIG. 1, of the same ejector device comprising said ejector lever and said ejector plunger, in a second setting for ejection of a long workpiece, and

[0026] FIG. 3 shows a view similar to the views of FIGS. 1 and 2, representing the same ejector device comprising said ejector lever and said ejector plunger, in a third final setting which corresponds to the final ejection position in which the long or the short workpiece is ejected.

DETAILED DESCRIPTIONS OF PREFERRED EMBODIMENTS

[0027] In the representations of FIGS. 1 to 3, identical parts are always indicated by the same reference numerals.

[0028] The die-side ejector device 12, shown in the Figures only by way of example, is part of a single-stage or multi-stage press (only part of which is shown) and serves to eject, from the die of the shaping press, the finished workpieces, for example screws or bolts or the like, manufactured from workpiece blanks (gradually, as the case may be) by means of a press carriage (not shown) guided in a reciprocatingly displaceable manner within a press frame 14 using carriage-side shaping tools (rams), which are also not represented, in stationary dies.

[0029] For this purpose, a carrier part in the form of a carriage or pusher 20 is guided, upwardly and downwardly displaceable, on a pressure plate 16, which is permanently attached to the press frame 14, between two guide rails 18 mounted on the pressure plate 16. In this case, the upward and downward movement of the carrier part 20 is transmitted—by a servomotor 22 flange-mounted on the pressure plate 16, via a pinion 24 rotatably connected to the shaft of said motor and via a rack 26 permanently connected to the carriage or pusher 20—to the latter. Using a blocking means (not shown), the carrier part 20 can be fixed on the pressure plate 16 in the operating position of the ejector device.

[0030] A two-armed ejector lever 32 comprising a longer lever arm 34a and a shorter lever arm 34b is pivotably supported within the drawing plane on a bolt 30 on the carrier part 20. A roll 38 is rotatably arranged on a bolt 36 on the smaller lever arm 34b of the ejector lever 32.

[0031] The front face of the ejector lever 32 facing the pressure plate 16 is realized as a curved cam 40 whose shape has been mathematically determined. The curved cam 40 of the ejector lever 32 cooperates with a pressure piece 44, whose concave contacting surface 46 represents a shaped surface corresponding to (segments) of the curved cam 40 of the lever 32. The pressure piece 44 itself is pivotably supported on a bolt 48 in the stationary pressure plate 16 so that, when the carrier part 20 is adjusted, the areal, complementary contact with the facing curved form of the curved cam 40 of the lever 32 is always definitely ensured, because the pressure piece 44 can thus also perform a slight pivotal movement.

[0032] As is evident from the Figures, the pressure piece 44 has a cylinder segment-shaped cross-section, with only the shaped surface 46 having a shape which differs from the cylindrical shape.

[0033] The pressure piece 44 is located within a receiving bore 42 of the pressure plate 16, with the diameter of said receiving bore 42 corresponding to the external diameter of the pressure piece 44.

[0034] Further, another two-armed lever 56, which serves as actuator lever for the ejector lever 32, is also pivotally supported on a bolt 54 on the press frame 14A roll 62 is rotatably supported on a bolt 60 on the longer arm 58 of the lever 56, said roll being part of a cam gear 64 and contacting the outside of a cam disk 70, which is arranged, immobilized against rotation, on an ejector shaft 68 of the shaping press, said shaft being driven by a motor (not shown) and supported within the press frame 14.

[0035] The shorter, offset arm 74 of the actuating lever 56 cooperates, by means of a contacting surface 76 provided thereon, with a compression spring 80 guided on a spring-supporting pin 78 and mounted under pretension, said spring being supported on the press frame 14 via a plate 82. In this way, the roll 62 always contacts the contour of the cam disk 70 by force.

[0036] The roll 38 arranged on the shorter arm 34b of the ejector lever 32 continuously contacts the front face, facing it, of the long arm 58 of the actuating lever 56 under the action of a compression spring 86 incorporated in the press frame 14 in a biased manner. For this purpose, the compression spring 86 is guided in a bore 88 extending horizontally in the press frame 14, on a spring-supporting pin 90, which is permanently connected with a cover plate 92 screwed onto the press frame 14. One end of the compression spring 86 contacts the cover plate 92, while the other end thereof contacts the front face of a guiding sleeve 96, in whose pocket hole 98 the free end of the spring-supporting pin 90 facing it is immersed. The guiding sleeve 96 itself is slidably guided in a bushing 100 mounted on the press frame 14 and arranged coaxially to the bore 88. A pressure piece in the form of a sliding shoe 104 comprising a calotte-shaped receiving shape 106 is pivotably mounted on the ball-shaped end 102 of the guiding sleeve 96.

[0037] In the graphical representation, there is provided, above the bore 88 and in the same vertical plane, a further cylindrical bore 110, in parallel with said bore 88, in the press frame 14, in which bore 110 one end of an ejector pin 112 is guided, in a slidably displaceable manner, in a bushing 114 permanently arranged within the press frame 14. The other, tapered end 116 of the ejector pin 112 is slidably guided in a further bushing 118, which is mounted in the cover plate 92, as well as in a stationary die 120 adjacent the cover plate 92. A further pressure piece in the form of a sliding shoe 124 is provided on the end 122 of the ejector pin 112, which end 122 is also ball-shaped, said sliding shoe 124 being pivotably mounted, with its calotte-shaped receiving shape 126, on the ball-shaped end 122 of the ejector pin 112.

[0038] The intermediate portion between the tapered end 116 of the ejector pin 112 and the larger-diameter portion of the ejector pin 112 guided in the bushing 114 is embodied as a pneumatic piston 130 which slides in the cylinder bore 110 of the press frame 14. For pneumatic cushioning, the press frame 14 is additionally provided with a pressure air supply line 132, which terminates in the cylinder bore 110, is constantly charged with pressure air and, together with the piston 130 in the cylinder bore 110, provides pneumatic cushioning.

[0039] The ejector lever 32 is provided, on its side facing both sliding shoes 104 and 124, with a planar surface 108 which serves as a counter-surface for contacting the sliding shoes 104 and 124 and on which said sliding shoes can execute sliding motions during adjustment or movement of the lever 32.

[0040] The operation of the represented die-side ejector device is as follows:

[0041] The ejector pin, acting as an ejector plunger, ejects a shaped workpiece 138 (FIG. 1), i.e., for example, one provided with a hexagon head, or a long workpiece 136 (FIG. 2), whose stem is respectively located in the bore of the stationary die 120 (FIG. 1) or 120′ (FIG. 2), from the latter in such a manner that the respective workpiece 136 or 138 is located in front of the die 120 or 120′ so that the front end of the ejector pin 112 is always in the same position Lo after the ejection operation, which condition is shown in FIG. 3. This is the position in which the ejected workpiece 136 or 138 (both of which are alternatively shown in FIG. 3) can be gripped and transported further.

[0042] So long as the workpiece 136 or 138 is being shaped, the front end of the ejector pin 112 needs to be in a retracted position for this purpose. In the case of the long workpiece 136, the end of the ejector pin 12 facing it needs to be in position L2 in the die 120 during the shaping operation (see FIG. 2), while the manufacture of the short workpiece 138 requires the end of the ejector pin 12 facing it to be in position L1 in the die 120′ (see FIG. 1).

[0043] In each retracted position L1 or L2 of the ejector pin 112 or in any intermediate position, the ejector pin 112 needs to transmit the pressing force generated for the shaping operation by the press carriage (not shown) to the stationary pressure plate 16. For this purpose, the pressing force is introduced into the pressure plate 16 via the ejector pin 112, the sliding member 124, the ejector lever 32 and the pressure piece 44. Thus, the concave shaped surface 46 of the pressure piece 44 always contacts the curved cam 40 of the ejector lever 32 in a precisely fitting manner, so that there is always an areal contact.

[0044] During shaping of the workpiece, the ejector lever 32 does not exert any force on the cam disk 70 of the cam gear 64 via the roll 38, the lever 56 and the roll 62.

[0045] Before the beginning of the ejecting operation of a shaped workpiece, the cam of the cam disk 70 is in a perpendicular position on the constantly rotating ejector shaft 68, i.e. in parallel with the pressure plate 16 of the press frame 14, as shown in FIGS. 1 and 2.

[0046] Upon further, counter-clockwise rotation of the ejector shaft 68 with the cam disk 70, the roll 63 of the cam gear 64 passes the idle portion of the cam disk 70, until the cam of the cam disk 70 begins to rise. The lever 56 then begins to pivot about the bolt 54 until the cam of the cam disk 70 has completed its rise and is perpendicular to the pressure plate 16 of the press frame 14, as shown in FIG. 3.

[0047] During this pivotal movement of the actuator lever 56, the ejector lever 32 is also simultaneously pivoted about the bolt 30 as a fulcrum, via the roll 38, which is in close front-face contact with the actuator lever 56 due to the force of the spring 86. This follower movement causes the shaped workpiece to be ejected from the die 120 or 120′ by the ejector pin 112. FIG. 3 shows a position after ejection, respectively, of a long workpiece 136 or of a short workpiece 138 from the die 120 or 120′ (namely in position Lo of the ejector pin 112).

[0048] During the subsequent drop of the cam flank of the cam disk 70, the roll 38 of the ejector lever 32, upon further rotation of the ejector shaft 68, then follows the actuator lever 56, as a result of the force exerted on the ejector lever 32 by the compression spring 86, until the ejector lever 32, and thus the ejector pin 112, again reaches its rear retracted, preset position L1 or L2 or any position between L1 and L2.

[0049] The curved cam 40 of the ejector lever 32 is designed such that it always contacts the complementary-shape counter-surface 46 on the pressure piece 44 in any imaginable positions between L1 and L2, in the rear end positions of the ejector pin 112 near the pressure plate. This serves to prevent the pressing force of the shaping operation from acting on the bolt 30, the roll 38, the actuating lever 56, the roll 62 and the cam disk 70, which force is detrimental to such structural elements and would destroy these parts in the course of time.

[0050] The setting of any desired starting position of the ejector pin 102 between L1 and L2 may be effected from any position of the ejector pin 112. For this purpose, the desired ejection stroke is input to the control of the shaping machine, upon which the servomotor 22 is excited and, upon release of the pusher lock (not shown), urges the carrier part 20 upward or downward via the pinion 24 and the rack 26 until the corresponding position of the fulcrum (bolt 30) of the ejector lever 32, and thus the rear starting position of the ejector pin 112, is reached, in order to obtain the desired ejection stroke. This ensures that the position Lo remains the same for all workpieces. Said adjustment of the fulcrum 30 of the ejector lever 112 may even be effected during operation of the shaping machine.

[0051] During adjustment of the fulcrum 30 of the ejector lever 112 by adjustment of the carrier part 20, the sliding shoes 104 and 124 slide along the planar front-face sliding surface, facing them, of the ejector lever 32 and, due to the bias resulting from the force of the compression spring 86 or of the pressure air piston 130 in the cylinder bore 110, they always contact said sliding surface 108 by force.

[0052] Thus, for example, an adjusting mechanism consisting of a worm, a wormgear or an adjusting screw might also very well be used instead of the pinion 24 and the rack 26, or use might easily be made also of a suitable compression spring instead of the air cushioning.

[0053] The invention has been described in language more or less specific as to structural and methodical features and by reference to detailed examples and methodologies. It is to be understood, however, that the invention is not limited to the specific features shown and described, since the means herein disclosed comprise preferred forms of putting the invention into effect, and the examples are not meant to limit the scope of the invention. It should be understood that variations and modifications may be made while remaining within the spirit and scope of the invention, and the invention is not to be construed as limited to the specific embodiments described or as shown in the drawings.

Claims

1. A die-side ejector device for workpieces in single-stage or multi-stage presses, wherein a stationary press die is provided on a press frame, said press die cooperating with a press ram for shaping a blank introduced into a bore of the press die, said device comprising an ejector pin slidably supported within a bore in the press frame, the die-side end of said ejector pin protruding into the bore of the press die and the other end thereof being biased against an ejector lever which is in turn pivotable, via an actuator lever driven by a cam gear, between a starting position, in which the die-side end of the ejector pin is retracted into the bore of the die, and a final ejection position, said ejector lever having its side facing away from the ejector pin in its starting position supported on a pressure piece mounted on the press frame, wherein the ejector lever is pivotably arranged on a carrier part, which is displaceable on the press frame, in a direction perpendicular to the longitudinal axis of the ejector pin and in parallel with the plane of pivot of the actuator lever, between two stops and which is provided, on its side facing the pressure piece, with a shaped surface for contact therewith, said shaped surface being designed for areal contact with a complementary shaped surface on the pressure piece, wherein both shaped surfaces maintain their areal, complementary contact in the starting position of the ejector lever even when the carrier part is being displaced.

2. The ejector device as claimed in claim 1, wherein the shaped surface is provided with a convex curvature on the ejector lever and the complementary, concave shaped surface is provided on an otherwise cylindrical pressure piece.

3. The ejector device as claimed in claim 2, wherein the pressure piece is pivotable about a central axis on a pressure plate mounted on the press frame.

4. The ejector device as claimed in claim 1, wherein the carrier part for the ejector lever is a displaceable supporting pusher or supporting carriage.

5. The ejector device as claimed in claim 1, wherein the ejector lever is provided as a two-armed lever, with the ejector pin contacting the end region of one lever arm and a rotatable roll being mounted on the end region of the other lever arm, said roll being supported against the actuator lever, which is provided, relative to the ejector lever, on the same side thereof as the ejector pin.

6. The ejector device as claimed in claim 1, wherein the cam gear for the actuator lever comprises a cam disk mounted on an ejector shaft, on which cam disk there runs a roll rotatably mounted on the free end of the actuator lever, said actuator lever being biased against the cam disk in order to urge the roll against the cam disk.

7. The ejector device as claimed in claim 1, wherein the ejector pin comprises a larger-diameter piston portion mounted in the bore in the press frame and provided as a displaceable piston and a subsequent smaller-diameter portion protruding into the bore of the press die, said portion being guided through a cover plate closing the bore in the press frame on the die side, and that the region between the larger-diameter piston portion and the cover plate of the bore in the press frame is connected to a pressure air supply line in order to bias the ejector pin against the actuator lever.

8. The ejector device as claimed in claim 1, wherein a device for biasing the ejector lever against the actuator lever is provided, said device being independent of the ejector pin.

9. The ejector device as claimed in claim 8, wherein the device for biasing the ejector lever consists of a piston arranged within a further bore in the press frame, said piston being spring-biased against the ejector lever and being supported by a sliding shoe on the side of the actuator lever facing the piston.

10. A press comprising:

a press frame;

a press ram;

a stationary press die provided on the press frame, wherein said press die cooperates with the press ram for shaping a blank introduced into a bore of the press die;

an ejector pin slidably supported within a bore in a press frame, said ejector pin having a die-side end, second end, and a longitudinal axis, the die-side end protruding into the bore of a press die;

an ejector lever, wherein the ejector pin second end is biased against said lever, the lever being pivotable, via an actuator lever, between a starting position, wherein the ejector pin die-side end is retracted into the bore of the press die, and a final ejection position, and wherein the ejector lever presents an opposing face in relation to the ejector pin, said opposing face in the starting position supported on a pressure piece mounted on the press frame;

a carrier part, upon which the the ejector lever is pivotably arranged and having a side facing the pressure piece, said carrier part displaceable on the press frame, in a direction perpendicular to the longitudinal axis of the ejector pin and in parallel with the plane of pivot of the actuator lever, between two stops, said side facing the pressure piece having a shaped surface, said shaped surface designed for areal contact with a complementary shaped surface of the pressure piece, wherein both shaped surfaces maintain their areal, complementary contact in the starting position of the ejector lever when the carrier part is being displaced.

11. The press as claimed in claim 10, wherein the shaped surface is provided with a convex curvature on the ejector lever and the complementary, concave shaped surface is provided on an otherwise cylindrical pressure piece.

12. The press as claimed in claim 11, wherein the pressure piece is pivotable about a central axis on a pressure plate mounted on the press frame.

13. The press as claimed in claim 10, wherein the carrier part for the ejector lever is a displaceable supporting pusher or supporting carriage.

14. The press as claimed in claim 10, wherein the ejector lever is provided as a two-armed lever, with the ejector pin contacting the end region of one lever arm and a rotatable roll being mounted on the end region of the other lever arm, said roll being supported against the actuator lever, which is provided, relative to the ejector lever, on the same side thereof as the ejector pin.

15. The press as claimed in claim 10, wherein the cam gear for the actuator lever comprises a cam disk mounted on an ejector shaft, on which cam disk there runs a roll rotatably mounted on the free end of the actuator lever, said actuator lever being biased against the cam disk in order to urge the roll against the cam disk.

16. The press as claimed in claim 10, wherein the ejector pin comprises a larger-diameter piston portion mounted in the bore in the press frame and provided as a displaceable piston and a subsequent smaller-diameter portion protruding into the bore of the press die, said portion being guided through a cover plate closing the bore in the press frame on the die side, and that the region between the larger-diameter piston portion and the cover plate of the bore in the press frame is connected to a pressure air supply line in order to bias the ejector pin against the actuator lever.

17. The press as claimed in claim 10, wherein a device for biasing the ejector lever against the actuator lever is provided, said device being independent of the ejector pin.

18. The press as claimed in claim 17, wherein the device for biasing the ejector lever consists of a piston arranged within a further bore in the press frame, said piston being spring-biased against the ejector lever and being supported by a sliding shoe on the side of the actuator lever facing the piston.

19. A die-side ejector device for workpieces in single-stage or multi-stage presses, wherein a stationary press die is provided on a press frame, said press die cooperating with a press ram for shaping a blank introduced into a bore of the press die, said device comprising an ejector pin slidably supported within a bore in the press frame, the die-side end of said ejector pin protruding into the bore of the press die and the other end thereof being biased against an ejector lever which is in turn pivotable, via an actuator lever driven by a cam gear, between a starting position, in which the die-side end of the ejector pin is retracted into the bore of the die, and a final ejection position, said ejector lever having its side facing away from the ejector pin in its starting position supported on a pressure piece mounted on the press frame, characterized in that the ejector lever is pivotably arranged on a carrier part, which is displaceable on the press frame, in a direction perpendicular to the longitudinal axis of the ejector pin and in parallel with the plane of pivot of the actuator lever, between two stops and which is provided, on its side facing the pressure piece, with a shaped surface for contact therewith, said shaped surface being designed for areal contact with a complementary shaped surface on the pressure piece, wherein both shaped surfaces maintain their areal, complementary contact in the starting position of the ejector lever even when the carrier part is being displaced.

20. The ejector device as claimed in claim 19, wherein the ejector lever is provided as a two-armed lever, with the ejector pin contacting the end region of one lever arm and a rotatable roll being mounted on the end region of the other lever arm, said roll being supported against the actuator lever, which is provided, relative to the ejector lever, on the same side thereof as the ejector pin.