Classifications

• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
  • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
  • B21D45/00—Ejecting or stripping-off devices arranged in machines or tools dealt with in this subclass
  • B21D45/02—Ejecting devices
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
  • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
  • B21J13/00—Details of machines for forging, pressing, or hammering
  • B21J13/08—Accessories for handling work or tools
  • B21J13/14—Ejecting devices
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
  • B21K—MAKING FORGED OR PRESSED METAL PRODUCTS, e.g. HORSE-SHOES, RIVETS, BOLTS OR WHEELS
  • B21K27/00—Handling devices, e.g. for feeding, aligning, discharging, Cutting-off means; Arrangement thereof
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
  • B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
  • B29C33/00—Moulds or cores; Details thereof or accessories therefor
  • B29C33/44—Moulds or cores; Details thereof or accessories therefor with means for, or specially constructed to facilitate, the removal of articles, e.g. of undercut articles
  • B29C33/442—Moulds or cores; Details thereof or accessories therefor with means for, or specially constructed to facilitate, the removal of articles, e.g. of undercut articles with mechanical ejector or drive means therefor
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
  • B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
  • B29C45/00—Injection moulding, i.e. forcing the required volume of moulding material through a nozzle into a closed mould; Apparatus therefor
  • B29C45/17—Component parts, details or accessories; Auxiliary operations
  • B29C45/40—Removing or ejecting moulded articles
  • B29C45/4005—Ejector constructions; Ejector operating mechanisms

Definitions

• the invention relates to an ejector device, which is particularly applicable in a press.
• the workpiece formed in a tool must be led out of the open tool after the forming process.
• These serve so-called ejector.
• these ejectors are usually located in the lower tool part. They comprise at least one ejector pin, which is in a rest position during the forming process. After carrying out the forming operation ⁇ and opening of the mold, the ejector pin is axially (e.g., vertically) moved, whereby it solves the workpiece from the mold and bring to transport height.
• the ejector device comprises an ejector drive in the form of a hydraulic cylinder.
• the piston rod of his piston drives an adjustable plate on which ejector pins rest. These press the workpiece out of the mold when the hydraulic cylinder is activated.
• the ejector device according to the invention is suitable for forming tools, in particular for stepped tools, in particular for massive forming as well as for casting or pressing tools.
• the ejector device has an ejector pin, to the drive device of which a first drive device and a second drive device belong.
• the first and the second drive device fulfill different tasks.
• the first drive means has a drive stroke which is less than the working stroke of the ejector pin.
• the first drive device can be designed so that it provides a particularly high driving force. It can thus be used to break loose the workpiece from the tool.
• the second drive device is designed in particular for a high drive speed. She takes over the drive of the ejector pin, when the workpiece is broken away and this leads at high speed in a position where it can be detected by a gripper or transfer device and transported on.
• the first drive device can also be considered as a "power unit" because of the large drive force it applies It suffices if the working stroke of the first drive device is a few millimeters, for example 20 mm, whereby the speed achieved by the first drive device can be relatively low
• the first drive means may consist of a drive and a high reduction gearbox
• the transmission may be a mechanical gearbox, a hydraulic gearbox or the like.
• the second drive means serves to overcome the greater part of the stroke length of the ejector pin. It can not only be designed for a maximum speed of, for example, up to 8 m / s or even more, but preferably also operate in a controlled way.
• the second drive means may comprise a servomotor or similar position controlled drive means.
• the ejector pin can be given a movement with a desired path-time profile in order to accelerate the workpiece, to track the opening tool and to bring it to a controlled position in the desired position.
• the workpiece can be controlled in this way and still moved out of the tool at high speed.
• an adjusting device is assigned in the ejector, with which the rest position of the ejector pin can be adjusted. This is particularly advantageous when, the ejector device is integrated into a press table on which the lower tool part is mounted.
• the adjustment is advantageous if a plurality of ejector devices are provided in a tool or a press, which are assigned, for example, different stages of a step tool. The ejector pin positions can thus be adapted to the workpiece shapes changing from stage to stage.
• the first drive device has an adjustable output member, which is adjustable by means of the adjusting device against the drive device.
• the output member may be connected via a thread with the first drive means. A rotation of the output member by the adjusting then causes an adjustment of the rest position of the first drive means.
• the ejector pin is connected to the first drive means via a contact surface. This acts as a printing surface.
• the first drive device can thus press the ejector pin against the workpiece.
• the ejector pin can be readily moved away from the first drive means. For this purpose, for example, serve the second drive means.
• the second drive device takes over the drive of the ejector pin at a predetermined position.
• the first drive device may be a hydraulic drive. It is also possible for the first drive device to comprise a preferably reducing gear, for example a lever gear. If a toggle mechanism is provided as the transmission, particularly high breakaway forces can be achieved with little effort. This is especially true if the o
• the toggle mechanism is in the extended position in the rest position of the first drive unit.
• the second drive device may be, for example, a linear motor direct drive of the ejector pin or another servomotor drive, which is in communication with the ejector pin, for example via a pinion rack connection or a similar gear.
• the second drive device may comprise one or more electric motors.
• FIG. 1 shows a press with a step-following tool in a schematic representation
• FIG. 2 shows the press table and the lower tool part of the press according to FIG. 1, in a sectional, vertically sectioned and extremely diagrammatic representation
• FIG. 3 shows an embodiment of the ejector of Figure 2 in a schematic representation
• Figure 5 shows a further embodiment of the ejector device in a schematic representation
• FIG. 6 shows a further embodiment of the inventive ejection device in a schematic representation.
• FIG. 1 schematically illustrates a press 1 which receives a step tool 2.
• the step tool 2 include an upper tool part 3 and a lower tool part 4.
• the upper tool part 3 is supported by a vertically moved up and down, carried in a press frame 5 corresponding plunger.
• the lower tool part 4 is mounted on a press table 7.
• the upper tool part 3 and the lower tool part 4 define between each other at least one, in a step tool but a plurality of mold cavities 8, 9, 10, 11, 12 with associated, provided on the upper mold part 3 punches 13, 14, 15, 16, 17th In each case a mold cavity 8 (9 to 12) and an associated punch 13 (14 to 17) form a forming stage of the step tool 2.
• the workpiece is by a not further illustrated, with the tool open between the tool parts 3, 4 cross transfer device from tool level to tool level transported further.
• Figure 2 illustrates the first stage of the lower tool part 3 in a schematic representation.
• a workpiece 18 is illustrated after completed forming process. It largely fills the mold cavity 8.
• Figure 2 further illustrates an ejector device 19 associated with the press 1 and the tool 2, respectively.
• This includes an ejector pin 20 and an ejector drive 21 which may be located in the tool part 4 or, as shown, the press table 7.
• the ejector pin 20 is arranged in an opening opening at the bottom of the mold cavity 8. ⁇ r is linearly displaceable in a direction coinciding with the direction of movement of the plunger 6 here vertical direction.
• the ejector 21 serves to operate the ejector 20 so that the Auswerferit 20 solves the workpiece 18 in the mold cavity 8 and from this preferably above the upper end surface 22 of the lower mold part 4 also lifts.
• the ejector drive 21 comprises a pressure pin 23 which, as shown, can abut with its end face against the lower end of the ejector pin 20.
• the pin 23 and the ejector pin 20 may also be integrally formed as a continuous machine part.
• the ejector 21 serves to selectively adjust the pressure pin 23 and with this the ejector pin 30 vertically.
• the ejector drive 21 comprises two drive devices, as illustrated by way of example in FIG.
• a first drive means 24 serves to generate a short-stroke movement, in the context of which the ejector pin 20 or the pressure pin 23 can be moved with great force.
• the first drive device 24 preferably has at least one output member 25 with a contact surface 26 on which an end face 27 of the pressure pin 23 rests, which can be understood as part of the Auswerfermas 20.
• first drive means 24 further includes a rotor 28 having a central threaded bore into which the output member 25 is screwed with its external thread 29. While the output member 25 may be non-rotatably supported by not further illustrated means in the longitudinal direction of the pin 23, the rotor 28, for example via axial pressure bearing 30 axially fixed while rotatably mounted.
• the rotor 28 may have permanent magnets 31 on its outer circumference.
• a stator 32 mounted in a stationary manner concentrically surrounding the rotor 28 forms with the permanent magnets 31 an electric motor, in particular a synchronous motor. gate.
• the output member can be moved with great force over a stroke Hl, which is less than the required stroke of the pressure pin 23rd
• the pressure pin 23 is also in communication with a second drive means 33 which is adapted to move the pin 23 over a predetermined stroke length H. To illustrate the stroke H is shown in Figure 3, the pin 23 in the rest position in a thick line and in the lifting position in a dashed line.
• To the second drive means 33 includes, for example, a synchronous motor 34 which drives a pinion 35.
• the pinion 35 meshes with a toothing 36 on an edge of the pin 23 which can form a rack so far.
• the ejector drive 21 described so far operates as follows:
• the plunger 6 After performing a press stroke, the plunger 6 initially moves upwards, whereby the upper tool part 3 is removed from the lower tool part 4, i. the tool 2 is opened. At this time, the situation according to FIG. 2 is found.
• the deformed workpiece 18 is firmly seated in the mold cavity 8 at the bottom thereof. It has to be led out of this mold cavity 8 and gripped by the transfer device, which is not further illustrated, and fed to a further processing, for example in the next following press stage.
• the ejector device is activated.
• at least the first drive means 24, if necessary but even the synchronous motor 34 of the second drive means 33 is activated.
• the first drive device 24 now moves, for example, by rotation of the rotor 28, the output member 25 at a relatively low speed upwards.
• the output member 25 thereby presses the pressure pin 23 or 20 with such a force against the workpiece 18, that this led out of his tight-fitting position and thus broke loose as it were.
• the required force can be a few 10 tons, up to 100 tons.
• the second drive means 33 takes over the further lifting of the workpiece 18.
• the synchronous motor 34 accelerates the pin 23 and via this the workpiece 18 to a speed in the top several meters per second ( For example, 8 m / s) can reach.
• the only short-stroke working first drive means 24 can not follow this movement.
• the end face 27 of the pin 23 lifts off from the pressure surface 26.
• the pin 23 passes through the stroke H very quickly, with which the workpiece 18 is above the end face 22.
• the second drive means 33 is arranged to move the pin 23 under the control of a not further illustrated control means and with this the workpiece 18 in a positionally controlled manner at high speed.
• the control device can predefine the synchronous motor 34 with a desired movement curve, so that the workpiece, for example, corresponds to the opening upper tool part 3 follows or even held in contact with this until the desired stop position is reached, in which the transfer can take over the workpiece 18.
• the ejector device 21 can be modified while maintaining the basic principle in a variety of ways.
• the second drive means 33 can be displaced out of the immediate vicinity of the pin 23.
• the second drive device 33a is arranged in Figure 4 next to the pin 23 at a certain distance to this.
• the synchronous motor 34a operates on a rack 37 which acts via an angle lever 38 on the lower end face 27 of the pin 23.
• the arrangement of Figure 4 can also serve to replace the first drive means 24, if it is designed accordingly strong.
• FIG. 5 illustrates another embodiment.
• the pin 23, here as a pin 23b is designed as a double toothed rack and is provided with two toothings 36a, 36b. These are arranged on different sides of the pin 23b and each mesh with pinions 35a, 35b which are driven by the synchronous motors 34a, 34b.
• the synchronous motors 34a, 34b form with their pinions 35a, 35b and the rack 23b, the second drive means 33b.
• the first drive device 24 is designed as a double toothed rack and is provided with two toothings 36a, 36b. These are arranged on different sides of the pin 23b and each mesh with pinions 35a, 35b which are driven by the synchronous motors 34a, 34b.
• the synchronous motors 34a, 34b form with their pinions 35a, 35b and the rack 23b, the second drive means 33b.
• the first drive device 24 is designed as a double toothed rack and is provided with two toothings 36a, 36
• a second stilt 45 engages one end 46 of a lever 47, the other end 48 is pivotally mounted.
• the end 48 is mounted on an adjusting device 49, which is formed for example by a Verstellxzenter 50. This can be adjusted by a not further illustrated adjustment specifically in different rotational positions to adjust the end 48 in its height.
• the abutment surface 26 is formed, on which the end face 27 of the rack 23 b rests.
• FIG. 5 illustrates the rest position of the ejector drive 21b.
• the toggle mechanism 21 In this rest position, the toggle mechanism 21 is in an extended position, i. the stilts 43, 45 form a straight line.
• the connecting rod 41 engages. If the synchronous motor 39 is activated, the connecting rod 41 and with this the pivot point 51 is moved to one side. This shortens the support length of the toggle mechanism 42, whereby the lever 47 is pivoted in Figure 5 upward (counterclockwise).
• the rack 23b is led out from the rest position from the perspective of the synchronous motor 39 with initially infinite and then gradually decreasing reduction. In this way, over the illustrated lever mechanism and the rack 23 b extremely large breakaway forces are transmitted to the workpiece. Once this is broken off, the synchronous motors 34a, 34b take over the conveyance and lead the workpiece out of the tool at high speed.
• the first drive means 24c according to the hydraulic principle.
• annular piston 52 which sits in a cylinder 53.
• the annular piston 52 divides at least one, preferably two working chambers 54, 55 from. They communicate with a hydraulic control device 56.
• the annular piston 52 has, for example, an internally threaded passage opening in which the output member 25 is seated. It can be selectively rotated against the rotationally secured annular piston 52.
• a servomotor 57 may be provided, which is axially loose via a sliding shaft 58, but rotatably connected to the output member 25.
• the rest position of the pressure surface 26 and thus of the pin 23 can be adjusted.
• the external thread 29 of the output member 25 thus forms together with the sliding shaft 58 and the servomotor 57, the adjusting device 49.
• a servomotor for rotation of the annular piston 52 may be provided against the output member 25.
• the pin 23 may in turn be designed as a rack. Its teeth 36 meshes, as already described in connection with Figure 3, with the pinion 35 of a suitable drive, such as a synchronous motor.
• the ejector 21c of Figure 6 operates as follows:
• Figure 6 illustrates the resting state.
• the annular piston 52 is in the lower position.
• the pin 23 rests with its lower end face 27 on the contact surface 26.
• the servomotor 57 By appropriate control of the servomotor 57, the height of the pin 23 can be adjusted with respect to its rest position.
• the directional control valve 59 belonging to the control device 56 switches to passage (lower channels 60) to the lower working chamber 55 to be connected to the hydraulic pressure generated by the hydraulic pump 61.
• the upper working chamber 54 is depressurized.
• the full force generated by the annular piston 52 is now transferred via the pin 23 on the workpiece so that it can be broken. As can be seen, but so only a short stroke can be performed.
• the servomotor which drives the pinion 35, takes over the drive of the pin 23, which thus lifts off from the output member 25 and runs upwards.
• the directional control valve 59 can also be switched to its reverse position (channels 62) to drive the ring piston 52 back into the position according to FIG ,
• the function of the adjusting device 49 can be taken over by the first drive device 24 in the embodiment according to FIG.
• the rest position of the output member can by the
• This rest position is determined by software, for example, by a control device 63, which is indicated only schematically in FIG. 3, which controls the first drive device 34 on the one hand and forms the adjusting device 49 on the other hand.
• the two drive devices have different strokes, actuating forces and actuating speeds.
• the first drive means serves to break loose the While the second serves to guide the workpiece out of its shape at a higher speed.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Moulds For Moulding Plastics Or The Like (AREA)
• Press Drives And Press Lines (AREA)
• Casting Devices For Molds (AREA)
• Casting Or Compression Moulding Of Plastics Or The Like (AREA)

Priority Applications (3)

Applications Claiming Priority (2)

Publications (1)

Family

ID=42126103

Family Applications (1)

Country Status (5)

Cited By (6)

Families Citing this family (7)

Citations (5)

Family Cites Families (8)

• 2009
  • 2009-04-17 DE DE200910017871 patent/DE102009017871B4/de not_active Expired - Fee Related
• 2010
  • 2010-03-06 CN CN201080016912.8A patent/CN102596527B/zh not_active Expired - Fee Related
  • 2010-03-06 ES ES201190065A patent/ES2407104B2/es not_active Expired - Fee Related
  • 2010-03-06 JP JP2012505064A patent/JP5659221B2/ja not_active Expired - Fee Related
  • 2010-03-06 WO PCT/EP2010/001402 patent/WO2010118799A1/de active Application Filing

Patent Citations (5)

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