EP3377311B1 - Weggebundene presse mit kulissenstein - Google Patents

Weggebundene presse mit kulissenstein Download PDF

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Publication number
EP3377311B1
EP3377311B1 EP16794605.2A EP16794605A EP3377311B1 EP 3377311 B1 EP3377311 B1 EP 3377311B1 EP 16794605 A EP16794605 A EP 16794605A EP 3377311 B1 EP3377311 B1 EP 3377311B1
Authority
EP
European Patent Office
Prior art keywords
path
motor
slide block
drive shaft
press according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP16794605.2A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3377311A1 (de
Inventor
Wilhelm Krieger
Dieter Fuchshofen
Norbert Gober
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
SMS Group GmbH
Original Assignee
SMS Group GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE102015222995.5A external-priority patent/DE102015222995A1/de
Application filed by SMS Group GmbH filed Critical SMS Group GmbH
Publication of EP3377311A1 publication Critical patent/EP3377311A1/de
Application granted granted Critical
Publication of EP3377311B1 publication Critical patent/EP3377311B1/de
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Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/26—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks
    • B30B1/266—Drive systems for the cam, eccentric or crank axis
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/26—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/40—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by wedge means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/0029—Details of, or accessories for, presses; Auxiliary measures in connection with pressing means for adjusting the space between the press slide and the press table, i.e. the shut height
    • B30B15/0035—Details of, or accessories for, presses; Auxiliary measures in connection with pressing means for adjusting the space between the press slide and the press table, i.e. the shut height using an adjustable connection between the press drive means and the press slide
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/06—Platens or press rams
    • B30B15/068—Drive connections, e.g. pivotal
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/32—Discharging presses

Definitions

  • the invention relates to a path-bound press according to the preamble of claim 1.
  • DE-OS-1 627 435 describes a forging press in which an eccentric of a drive shaft engages in an opening of a sliding block.
  • the sliding block is supported with an upper, convex side and a lower, convex side against a correspondingly concave surface of a sliding block.
  • the sliding block oscillates around a pendulum axis that runs through a lower area of the sliding block.
  • WO 2007/091935 A1 describes a drive for a press in which a first motor drives a flywheel that can be coupled to the press and in which a second motor is also provided to drive the press.
  • JP-S57 14499 A discloses a path-bound press according to the preamble of claim 1.
  • Such a design of the press drive allows a particularly low design of the drive, whereby, for example, relatively small flywheel diameters can be used. This allows an ideal combination with a power transmission using a sliding block, since such power transmissions can also be implemented with a low installation height.
  • the first motor essentially serves to drive the flywheel and at least partially replenish the energy extracted from the flywheel.
  • the second motor essentially serves to accelerate and/or decelerate the drive shaft decoupled from the flywheel in a state decoupled from the flywheel.
  • the second motor can also be used to introduce additional drive energy when coupled.
  • the deceleration energy that occurs during deceleration can be fed to the first motor via a converter in a possible detailed design.
  • Motors in the sense of the present invention are understood to mean electric motors.
  • a sliding block is understood to mean an element that can be moved in a forced manner relative to a sliding block surface.
  • the sliding block surface comprises in particular the pressure-side surface and the tension-side surface for guiding the sliding block.
  • a driver is understood to mean, for example, an eccentric or a crank pin.
  • the driver is preferably an eccentric of the drive shaft, which runs, for example, with a circular circumference in an opening in the sliding block.
  • a link is understood to be a movable component of the press that absorbs and transmits a working pressure from the link block during a press stroke or forming process.
  • the link can in principle be designed as a common component with a ram of the press. In other embodiments, however, another gear of any design, for example a wedge deflection, can be provided between the link and the ram.
  • the link In the area where the force is absorbed in the pressure direction, the link preferably has a pressure piece that has material properties optimized for contact with the link block.
  • a press in the sense of the invention generally relates to a press for forging, punching, deep drawing or any other forming process for which path-bound presses are used.
  • the clutch is closed in normal operation when a drive-side and an output-side speed on the clutch are at least approximately the same, with the speeds being adjusted via a targeted control of the second motor. This allows a significant reduction in wear on the clutch.
  • the first motor and the flywheel are arranged coaxially to one another. They are preferably integrated as a structural unit to form a flywheel motor. Such a flywheel motor advantageously dispenses with a space-consuming belt drive and additional motor console.
  • the motor and the flywheel are arranged coaxially and connected to one another via a gear, preferably a planetary gear, so that transmission ratios can also be implemented depending on requirements. This can enable particularly small flywheel masses.
  • flywheel it is generally advantageous for the flywheel to be coupled to the drive shaft without a gear ratio, with the flywheel being arranged in particular concentrically to the drive shaft.
  • Such a simple design without a reduction gear can be integrated particularly advantageously if the flywheel can be designed with a sufficiently small diameter. This is again made possible by the drive concept according to the invention.
  • the second motor is designed as a torque motor arranged concentrically to the drive shaft.
  • a torque motor is generally understood to mean a A torque motor is a high-torque, high-pole motor that usually runs on a hollow shaft. Torque motors also have a high torque even when stationary.
  • a brake on the drive shaft is provided concentrically to the torque motor and overlaps the torque motor in the axial direction.
  • the brake can be placed in particular in the area of a hollow shaft of the torque motor in order to also use this installation space.
  • the brake can be a mechanical brake for generating frictional heat or an electrical recuperation brake.
  • the brake can be a holding brake to ensure that the press comes to a standstill when it is not in use. It can particularly preferably be a spring-loaded brake that can be opened pneumatically and closed hydraulically and/or electromagnetically.
  • the drive shaft runs through an angle of rotation of more than 360°, starting from a stationary start position via the pressing stroke to a stationary stop position.
  • this is an angle of rotation between 370° and 450°. This allows a larger acceleration path before the actual pressing process or a larger braking path after the actual pressing process, so that the corresponding motors and brakes can be dimensioned smaller accordingly. This applies in particular to the second motor.
  • a main bearing point of the drive shaft is lubricated by means of a circulating oil lubrication system.
  • the pressure-side sliding surface on the sliding block and/or the tension-side sliding surface of the sliding block is designed to be straight.
  • the straight shape of a pressure-side sliding surface or both pressure-side sliding surfaces enables simple manufacture of the sliding block.
  • the pressure-side sliding surface on the sliding block has a concave or convex curvature, with the tension-side sliding surface of the sliding block having a different, concave or convex, curvature.
  • the concave or convex shape of the pressure-side sliding surface makes it easy to achieve a force transmission through the sliding block that corresponds to a slider-crank mechanism.
  • a large contact surface is achieved in the area of the sliding surface, so that a design for large pressing forces can be easily achieved. Overall, this results in an optimized force-displacement curve.
  • the pressure-side, concave curvature and the tension-side, convex curvature can each be designed in the shape of a circular arc.
  • the curvatures are preferably arranged concentrically around the same point through which a pendulum axis of the sliding block also runs. Both sliding surfaces form positively guiding sliding block surfaces of a sliding block gear for the sliding block.
  • the sliding block has a concave sliding surface on the pressure side and a convex sliding surface on the tension side. This corresponds to the kinematics of a slider-crank mechanism, in which the dead center of a working stroke or pressing process is in an extended position of the slider-crank mechanism.
  • the sliding block has a convex sliding surface on the pressure side and a concave sliding surface on the tension side. This corresponds to the kinematics of a slider-crank mechanism, in which the dead center of a working stroke or pressing process is in a cover position of the slider-crank mechanism.
  • the design of a path-bound press according to the invention generally allows for a low overall height. This leads to shorter spring lengths for the column, ram and/or link of the press. This improves the rigidity compared to conventional eccentric presses of the same column design.
  • the design according to the invention makes it possible to have a particularly long rigid unit consisting of the link and ram for a given height of the press. This allows particularly good lateral guidance of the ram or the rigid unit, even with high pressing forces.
  • the sliding block executes a pendulum movement about a pendulum axis, with the pendulum axis being arranged outside the sliding block.
  • the pendulum axis is preferably arranged in a fixed position relative to the sliding block.
  • the sliding block then causes a movement transmission in the manner of a slider-crank mechanism with respect to the pendulum axis or with respect to the sliding block.
  • a different forced guidance of the sliding block is also conceivable depending on the requirements, so that the kinematics of a slider-crank mechanism is only one of various possible movement transmissions.
  • the invention is not limited to the specifically described variants of slider-crank mechanisms.
  • Such a design of the gear of the press according to the invention allows a high ratio between a pressing force acting in the guide direction of the pressure piece and a normal force acting perpendicular to it. A certain normal force is desired in order to ensure that the link and/or the ram are well positioned on a lateral guide.
  • a large inverse push rod ratio 1/Lambda is possible without the overall height of the press having to be increased. Due to the above-mentioned features, similar pressure contact times (parameter: lambda) as with conventional eccentric presses with pressure rods can be achieved, even with a low installation height and correspondingly good rigidity.
  • the pendulum axis is on the side of the compression direction with respect to the shaft axis.
  • the compression contact time is the same as with conventional presses with a pressure rod for the same rotation time.
  • the pendulum axis is on the side of the tension direction with respect to the shaft axis.
  • the compression contact time is higher for the same rotation time than with conventional presses with a pressure rod, but this can be an advantage with special forming processes or materials.
  • an adjusting element preferably in the form of an adjustable, rotatable eccentric ring, is arranged between the driver and the sliding block.
  • Such an adjusting element can be used, for example, to adjust the height of a tappet.
  • the link is moved substantially in line with a ram of the press during the press stroke. This corresponds to a linear and direct transmission of the press force.
  • a force deflection takes place between the link and a ram of the press.
  • the force deflection can preferably take place by means of a wedge. This allows the general advantages of a wedge press to be combined with the advantages of a press according to the invention.
  • an ejection mechanism which is fixed in position relative to the guide rail and has an ejector which can be moved relative to the guide rail and acts on a workpiece, the ejection mechanism being actuated by the movement of the guide rail.
  • This allows a workpiece to be ejected easily and effectively after a pressing process.
  • Such an ejection mechanism is particularly preferably combined with a guide rail of the second embodiment, which has a convex sliding surface on the pressure side. With otherwise identical dimensions, this means that the guide rail has a greater path in the area of the sliding surface on the pressure side, which allows a particularly easy and effective transfer of movement to the ejector.
  • the ejector can be actuated, for example, by a ramp, cam or similar structure formed on the guide rail, which actuates the ejector against a restoring spring force when the drive shaft reaches a corresponding position.
  • a gear can be arranged between the sliding block and the ejector so that the force and movement of the ejector are further optimized.
  • the gear can be a linkage gear, a bell crank or similar.
  • the path-bound press according to the invention according to the embodiment according to Fig.1 comprises a drive shaft 1 with a shaft axis W, which is divided into two Main bearings 2 are rotatably mounted relative to a press frame 3.
  • the main bearings 2 preferably have circulating oil lubrication.
  • the drive shaft 1 has an eccentric driver in the form of an eccentric 4.
  • the eccentric 4 which is circular in cross-section, has an eccentric axis E which is offset by a radial distance R from the shaft axis W.
  • the eccentric 4 passes through a sliding block 5 in a bore 6 corresponding to the diameter of the eccentric.
  • the sliding block is made up of several parts.
  • the sliding block 5 is in turn guided in a guide 7.
  • the guide 7 is designed as a housing that can be moved relative to the press frame 3.
  • the guide 7 comprises a pressure piece 8 on a pressure side, on which a pressure-side sliding surface 8a is formed.
  • a tension-side sliding surface 7a is formed on the guide.
  • the sliding block 5 has a pressure-side sliding surface 5a, which rests on the sliding surface 8a of the pressure piece 8, and a tension-side sliding surface 5b, which rests on the tension-side sliding surface 7a of the sliding block 7.
  • the pressure-side sliding surface 5a is concavely formed on the sliding block 5.
  • the tension-side sliding surface 5b is convexly formed on the sliding block 5.
  • the sliding surfaces 5a, 5b, 7a, 8a are each formed as sections of a cylinder surface, with the cylinder axes running parallel to the shaft axis W.
  • the sliding surfaces 5a, 5b, 7a, 8a run concentrically around a pendulum axis P of the sliding block 5 that is parallel to the shaft axis W.
  • the cylinder axes of the cylinder surfaces to which the Sliding surfaces 5a, 5b, 7a, 8a each form cutouts, together with the pendulum axis P.
  • the pendulum axis P is therefore located on the pressure side and outside the sliding block, since the pressure-side sliding surface 5a of the sliding block 5 is concavely shaped.
  • the sliding block 5 undergoes a forced pendulum movement around the pendulum axis P.
  • the pendulum axis P is fixed in space with respect to the guide 7 or the pressure piece 8.
  • the guide 7 and the pressure piece 8 provided on it are accommodated by lateral guides 9 in which they can each be moved linearly in a direction perpendicular to the shaft axis W.
  • a pressing stroke is carried out in which the driving force of the drive shaft 1 acts on the pressure piece 8 via the sliding block 5.
  • the driving force of the drive shaft 1 acts on the tension-side sliding surface 7a of the sliding block 7 via the sliding block 5, so that the sliding block 7 and the pressure piece 8 are brought back in the opposite direction to the pressing stroke.
  • clamping devices 7b are arranged on the underside of the guide 7, with which a press ram and/or a tool holder and/or a tool can be attached. These perform identical movements to the guide 7 or the pressure piece 8.
  • the guide 7 or the pressure piece 8 perform a movement similar to that of a slider crank drive.
  • a slider crank drive is the transmission of motion between the piston and the crankshaft in a conventional combustion engine.
  • the quantities that characterize the movement are the radial distance R on the one hand and a distance L between the pendulum axis P and the eccentric axis E.
  • the ratio R:L corresponds to the push rod ratio lambda.
  • the dead center of the working stroke corresponds to the extended position of an analog slider crank mechanism. This means that the distances R and L are collinear and one behind the other at the lowest point of the tool.
  • the dead center of the working stroke is also referred to as the bottom dead center.
  • the maximum tappet speed In contrast to a pure sinusoidal drive (e.g. a sliding block sliding horizontally in the guide rail with a flat sliding surface on the pressure side), the maximum tappet speed only occurs after 90° after TDC (top dead center).
  • a pure sinusoidal drive e.g. a sliding block sliding horizontally in the guide rail with a flat sliding surface on the pressure side
  • Fs is the total compressive force exerted by the sliding block 5.
  • Fs lies on a straight line that runs perpendicularly through the eccentric axis E and the pendulum axis P.
  • Fp is the force component of Fs that acts in the direction of the press stroke or on the workpiece. In the specific design of the press according to Fig.1 This is the vertical force component.
  • Fn is the force component of Fs that is perpendicular to Fp and also perpendicular to the guides 9 or the direction of the press stroke.
  • the behavior of the moving parts in the guides 9 is largely determined by Fn.
  • a respective angle WF between Fp and Fs is an expression of the crank angle and the ratio L:R. Due to the selected ratio L:R, the angle WF in the present example of a press is relatively small.
  • a drive of the drive shaft 1 comprises a first motor 10, a flywheel 11 that can be driven by the first motor 10, and a second motor 12.
  • the flywheel 11 can be detachably coupled to the drive shaft 1 via a clutch 13.
  • the second motor 12 drives the drive shaft 1 directly. In one possible operating mode, deceleration or braking with this drive is not carried out via a brake, but via the second motor 12.
  • the flywheel 11 and the first motor 10 are combined to form a structural unit in the form of a flywheel motor 14.
  • the first motor 10 and the flywheel 11 are arranged coaxially to one another and to the shaft axis W of the drive shaft 1.
  • the motor 10 and the flywheel 11 are directly connected to one another.
  • a transmission for example by means of a gear or a belt drive, does not take place here.
  • a transmission can be provided between the flywheel and the first motor, for example by means of a planetary gear.
  • the clutch 13 is arranged directly on the flywheel motor 14 and is also in a concentric or coaxial position on the shaft axis W. Flywheel motor 14 and clutch 13 are arranged on the same of two ends of the drive shaft 1.
  • the second motor 12 is arranged at the second end of the drive shaft 1, opposite the main bearing 2.
  • the second motor 12 is also positioned coaxially to the shaft axis W above the drive shaft 1. It drives the drive shaft directly and without gearing.
  • the second motor 12 is designed as a torque motor. The second motor 12 therefore has a high torque even when stationary.
  • a brake 15 of the drive is positioned concentrically and overlapping the second motor 12 in the axial direction.
  • the brake is positioned predominantly in a hollow shaft of the second motor 12, whereby this installation space is used optimally.
  • the brake can be designed as an electrical recuperation brake and/or as a mechanical brake that generates frictional heat.
  • the brake 15 is preferably spring-loaded and serves as a safety element in possible operating mode when the press is at a standstill. It can be opened pneumatically or closed hydraulically and/or electromagnetically.
  • the view Fig.2 makes it clear that the flywheel 11 has a sufficiently small diameter so as not to overlap in height with a working area 16 of the press. This allows optimal access to the working area 16
  • the flywheel 11 is permanently held at a desired speed by the first motor 10.
  • the second motor 12 serves to accelerate the drive shaft 1 from a resting starting position to a speed that is the same or at least almost the same as the flywheel before a pressing process, while the clutch 13 is still disengaged. If the speed difference is sufficiently small, the clutch 13 is then engaged or closed so that little or no friction loss occurs at the clutch. Accordingly, the clutch is relatively small.
  • the subsequent pressing stroke and forming process of a workpiece brakes the drive shaft 1 and energy is extracted from the flywheel 11.
  • the first motor 10 and the second motor 12 work together at high power in order to at least partially compensate for the energy extraction.
  • the flywheel is relatively small.
  • the drive shaft 1 is decoupled again from the flywheel 11. With the aid of the brake 15, and if necessary also by reversing the second motor 12, the drive shaft 1 is then brought to a standstill.
  • an electronic control of the press is designed in such a way that the drive shaft 1, starting from the stationary start position, passes through a rotation angle of more than 360° through the press stroke/forming process to the stationary stop position.
  • the rotation angle is preferably between 370° and 450°.
  • the angle of rotation is approximately 390°.
  • the drive shaft is first rotated back by approximately 30° against the working direction, i.e. 30° before top dead center, before acceleration in the working direction by the second motor 12. This does not cause a collision or impairment of the working area 16, but significantly increases the available acceleration angle for the subsequent rotation of the drive shaft in the working direction.
  • the second motor 12 can be designed to be relatively small.
  • Fig.3 shows the press Fig.1 in a sectional view with section plane II-II running perpendicular to the drive shaft.
  • An additional adjusting element 17 is provided, by means of which the height of the sliding block 5 can be adjusted. This adjustment can also be made during operation. In one possible operating mode, the adjustment can be made in stages between two successive strokes.
  • the adjusting member 17 comprises an eccentric ring 18 which is arranged between the bore 6 in the sliding block 5 and the eccentric 4 of the drive shaft 1.
  • the eccentric ring 18 can be rotated in its seat via an actuator 19 so that the bore receiving the eccentric 4 changes its position with respect to the sliding block 5.
  • Fig.2 shows a clamp 17a of the adjusting element 17.
  • the clamp 17a can be opened hydraulically.
  • the closing of the clamp 17a can be hydraulically or mechanical (self-locking) or combined hydraulic and mechanical.
  • Fig.5 shows a second embodiment of a press according to the invention.
  • a ram and/or tool of the press is not moved directly and linearly by the link 7.
  • a force deflection is provided between the pressure piece and a ram of the press.
  • the force deflection takes place by means of a wedge 20, which is displaceable relative to a frame-fixed support surface 21 inclined to the direction of the press stroke.
  • the wedge 20 is firmly connected to the link 7.
  • a ram 22 of the press rests displaceably on a side of the wedge 20 opposite the support surface 21.
  • the press stroke HP is considered to run in the direction of this offset in the sense of the invention.
  • a movement HS of the ram 22 of the press is redirected by approximately 120° to the press stroke HP of the link 7.
  • Such a wedge drive can achieve a particularly uniform force distribution across the width of the ram.
  • the second embodiment does not show any changes to the example according to Fig.1 on.
  • the sliding block is formed according to a second variant.
  • the pressure-side Sliding surface 5a on the sliding block 5 is convexly shaped, in contrast to the concave shape in the previously described examples.
  • the tension-side sliding surface 5b on the sliding block 5 is also shaped in the opposite way to the previous examples, i.e. concave.
  • the corresponding sliding surfaces 7a, 8a on the sliding block are also curved in the opposite way.
  • the sliding surfaces 5a, 5b, 7a, 8a are as in the first variant according to Fig.4 each formed as cutouts of a cylinder surface, with the cylinder axes running parallel to the shaft axis W.
  • the sliding surfaces 5a, 5b, 7a, 8a in turn run concentrically around a pendulum axis P of the sliding block 5 that is parallel to the shaft axis W.
  • the pendulum axis P is therefore also located outside the sliding block 5. Unlike in the first variant, the pendulum axis P in the second variant is on the tension side with respect to the sliding block 5. For the sliding block 5, rotation of the drive shaft 1 again results in a forced pendulum movement around the pendulum axis P.
  • the second variant also corresponds to an analog slider-crank mechanism with the characteristic dimensions L (distance between the pendulum axis P and the shaft axis W) and R (distance between the eccentric axis E and the shaft axis W).
  • the dead center of the working stroke corresponds to a cover position of an analog slider-crank mechanism. This means that the distances R and L are collinear and lie one above the other at the lowest point of the tool.
  • an ejection mechanism 23 is integrated into the press, which is actuated by means of the movement of the sliding block.
  • the ejection mechanism comprises an ejector 24, which runs linearly displaceably in a guide of the ram 22 and can press against a workpiece (not shown) at the lower end of the ram.
  • the ejector 24 After a pressing process, the ejector 24 is moved against the workpiece by means of a mechanical positive guide and pushes it out of a tool (not shown). In this way, a reliable workpiece change is made possible in a simple manner.
  • the ejector 24 is actuated by means of a ramp 27 on the sliding block 5.
  • the ramp 27 rests against a head 28 of the ejector 24, which is in the form of a ball.
  • the sliding block performs its pendulum movement around the pendulum axis P, sliding along the pressure-side sliding surfaces 5a, 8a.
  • the ejector 24 is initially in a position reset by means of a spring 29, in which it does not press on the workpiece.
  • the ramp 27 begins to press in the ejector 24 via the ball 28.
  • Fig.7 Approximately the starting point of this ejection process is shown, with the sliding block 5 in the central position and the tappet 22 in a bottom dead center.
  • the sliding block 5 moves in the illustration according to Fig.7 further to the left and the ramp 27 moves the ejector 24 relative to the plunger 22 or to the guide 7 against the workpiece.
  • the ejector 24 performs a movement by a stroke HA against the force of the spring 29.
  • the ejector mechanism is illustrated using the first variant of the sliding block 5 with a concave sliding surface 5a on the pressure side.
  • the ejector mechanism can also preferably be combined with the second variant of the sliding block 5 with a convex sliding surface 5a on the pressure side. This has the advantage that the linear path of the sliding block 5 along the sliding surface 5a is larger with otherwise identical dimensions of the press, which allows a less steep design of the ramp 27.
  • the stroke HA of the mechanical ejector 23, 24 can be increased. This means that the large force required for ejection is applied by the mechanical ejector with a small stroke HA.
  • the hydraulic piston increases the stroke HA by the stroke HH.
  • the hydraulic piston 25 is operated via a valve with hydraulic control 34.
  • the gear 30 is designed as a reversing lever, which is mounted in a rotary bearing or pivot bearing 31 on the sliding block 7.
  • the sliding block 5 is connected to the reversing lever in a rotary bearing 32, with the pivot point of the rotary bearing 32 being aligned with the sliding surface 5a.
  • the rotary bearing 32 can be designed as a cam roller. The pivoting movement of the reversing lever is then positively controlled via the cam roller 32 by the cassette guide 33 arranged on the sliding block 5.
  • a ramp 27 is formed on the reversing lever 30, which, as in the previous example, engages the ejector 24.
  • the reversing lever in particular enables a longer ramp in order to better control the ejector 24.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Control Of Presses (AREA)
  • Forging (AREA)
  • Presses And Accessory Devices Thereof (AREA)
EP16794605.2A 2015-11-20 2016-11-10 Weggebundene presse mit kulissenstein Active EP3377311B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102015222994 2015-11-20
DE102015222995.5A DE102015222995A1 (de) 2015-11-20 2015-11-20 Weggebundene Presse mit Kulissenstein
PCT/EP2016/077224 WO2017084953A1 (de) 2015-11-20 2016-11-10 Weggebundene presse mit kulissenstein

Publications (2)

Publication Number Publication Date
EP3377311A1 EP3377311A1 (de) 2018-09-26
EP3377311B1 true EP3377311B1 (de) 2024-05-01

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EP16795009.6A Active EP3377312B1 (de) 2015-11-20 2016-11-10 Weggebundene presse mit kulissenstein

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US (2) US11084240B2 (enrdf_load_stackoverflow)
EP (2) EP3377311B1 (enrdf_load_stackoverflow)
JP (2) JP6656374B2 (enrdf_load_stackoverflow)
KR (2) KR102122225B1 (enrdf_load_stackoverflow)
CN (2) CN108472904B (enrdf_load_stackoverflow)
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CN109848348B (zh) * 2018-12-29 2023-10-20 武汉新威奇科技有限公司 一种数控直驱式电动螺旋压力机
JP7304842B2 (ja) 2020-09-28 2023-07-07 アイダエンジニアリング株式会社 プレス機械
CN113893441B (zh) * 2021-08-26 2023-04-21 中国科学院自动化研究所 一种介入手术递送装置
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MX2018006187A (es) 2018-08-01
BR112018010151A2 (pt) 2018-11-21
US11186056B2 (en) 2021-11-30
KR20180079402A (ko) 2018-07-10
EP3377312B1 (de) 2024-04-10
EP3377312A1 (de) 2018-09-26
US20180345614A1 (en) 2018-12-06
KR102099727B1 (ko) 2020-04-10
BR112018010151A8 (pt) 2019-02-26
CN108472904A (zh) 2018-08-31
BR112018010223A8 (pt) 2019-02-26
CN108472904B (zh) 2020-04-28
CN108472903B (zh) 2020-10-09
CN108472903A (zh) 2018-08-31
EP3377311A1 (de) 2018-09-26
US11084240B2 (en) 2021-08-10
JP6667635B2 (ja) 2020-03-18
JP2018534148A (ja) 2018-11-22
ES2980777T3 (es) 2024-10-03
US20180326683A1 (en) 2018-11-15
WO2017084952A1 (de) 2017-05-26
WO2017084953A1 (de) 2017-05-26
KR102122225B1 (ko) 2020-06-15
BR112018010223B1 (pt) 2022-06-28
JP2018538143A (ja) 2018-12-27
ES2981739T3 (es) 2024-10-10
BR112018010151B1 (pt) 2022-06-28
KR20180077237A (ko) 2018-07-06
JP6656374B2 (ja) 2020-03-04
MX2018006191A (es) 2018-08-01

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